CN110193792B - Phase difference hydraulic elastic clamp device - Google Patents
Phase difference hydraulic elastic clamp device Download PDFInfo
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- CN110193792B CN110193792B CN201910353836.2A CN201910353836A CN110193792B CN 110193792 B CN110193792 B CN 110193792B CN 201910353836 A CN201910353836 A CN 201910353836A CN 110193792 B CN110193792 B CN 110193792B
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
- B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING OR HOLDING
- B25B11/00—Work holders not covered by any preceding group in the subclass, e.g. magnetic work holders, vacuum work holders
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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
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
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Abstract
A phase difference hydraulic elastic clamp device belongs to the technical field of fatigue testing devices. The device comprises a handle and a rotating shaft which is connected with the handle in a matching way, wherein a first cam and a second cam are coaxially arranged on the rotating shaft, a phase difference is arranged between the first cam and the second cam, and an opening stable pressure maintaining area are also synchronously arranged on the first cam and the second cam; the device also comprises a reversing valve and a clamping tool. According to the technical scheme of the phase difference hydraulic elastic clamp device, when the direction is changed to the reversing port A, hydraulic oil enters the piston cavity II, the push plate moves leftwards, and the clamping plate is loosened; when the direction is changed to the direction changing port B, hydraulic oil enters the piston cavity I, the push plate moves rightwards, and the clamping plate is clamped; the use is simple and convenient.
Description
Technical Field
The invention belongs to the technical field of fatigue testing devices, and particularly relates to a phase difference hydraulic elastic clamp device.
Background
The existing hydraulic elastic clamp device needs to push the reversing valve by hand, and is very manual. Current manual switching-over valve is by manual going to draw, and the frequency of drawing is very high, and manual switching-over valve presss from both sides the dress for pressing from both sides the dress use, and the bending is lived when pressing from both sides, and when loosening, the valve is opened, and the operative employee probably needs two three minutes to draw once, and the operation is tired, and work efficiency is low. The valve core of the existing manual reversing valve does reciprocating motion and can not rotate. The valve core and the valve sleeve are provided with gaps, if the valve core and the valve sleeve are static, the valve core can fall down, the valve core and hydraulic oil have viscosity, the valve has viscous resistance in the valve, the oil is dirty, the resistance is higher, the pulling force needs to be increased, and the working efficiency is obviously reduced.
Disclosure of Invention
Aiming at the problems in the prior art, the invention aims to design and provide a technical scheme of a phase difference hydraulic elastic clamp device, a handle is pushed, a first cam is arranged on an outer ring of a second cam and forms a phase difference when rotating synchronously, when the device operates, a first rotary push small valve can be opened first, a main valve core is opened later, the first rotary push small valve moves rightwards, a high-pressure lead port is communicated with a high-pressure cavity, a low-pressure lead port and a pressure compensation lead port are communicated with a pressure compensation cavity, a right H cavity communicated with the pressure compensation cavity is high-pressure oil and also provides a leftward thrust for the main valve core, so that labor is saved when the handle is pushed manually; the main valve core can be pushed leftwards and rightwards, and can also rotate under the driving of the rotating disk, and the rotary push small valve can also rotate under the action of hydraulic oil sprayed from the rotary nozzle, so that the main valve core and the rotary push small valve cannot be clamped, the viscous resistance is reduced, the handle is pulled by hand easily and labor-saving, and the working efficiency is obviously improved; under the combined action of the main valve core and the rotary push small valve, the invention obviously reduces the labor intensity and improves the working efficiency. Because the edges of the first cam and the second cam are provided with the stable pressure-retaining area of the port A and the stable pressure-retaining area of the port B which have the same structure, the reversing valve is switched to the reversing port A to be kept for a period of time, and then switched to the reversing port B to be kept for a period of time; when the piston is reversed to the reversing port A, hydraulic oil enters the piston cavity II, the push plate moves leftwards, and the clamping plate is loosened; when the direction is changed to the direction changing port B, hydraulic oil enters the piston cavity I, the push plate moves rightwards, and the clamping plate is clamped; the use is simple and convenient.
The hydraulic elastic clamp device with the phase difference is characterized by comprising a handle and a rotating shaft which is in matched connection with the handle, wherein a first cam and a second cam are coaxially arranged on the rotating shaft, the phase difference is arranged between the first cam and the second cam, and a stable pressure maintaining area are also synchronously arranged on the first cam and the second cam;
the reversing valve is a valve body formed by connecting a first shell, a second shell and a third shell in a matching way, a first oil return cavity and a third backflow port are arranged in the first shell, a main valve core is arranged in the second shell, a reversing valve sleeve is arranged in the middle of the main valve core in a matching way, a first oil return cavity, a reversing cavity, a high-pressure cavity, a reversing cavity, a second oil return cavity, a left H cavity, a pressure compensation cavity and a right H cavity are formed between the main valve core, the reversing valve sleeve and the second shell, and a first backflow port, a reversing port, a high-pressure oil inlet, a reversing port and a second backflow port are correspondingly arranged on the second shell; when the main valve core moves rightwards, the first oil return cavity is communicated with the reversing cavity; when the main valve core moves leftwards, the oil return cavity II is communicated with the reversing cavity; the left end of the main valve core is tightly matched with a rotating disc, the rotating disc is installed in the oil return cavity, the main valve cavity of the main valve core is communicated with a rotating disc cavity of the rotating disc, a rotary nozzle communicated with the rotating disc cavity is arranged on the rotating disc, a valve sleeve is arranged between the main valve core and the first shell and between the main valve core and the second shell in a matched mode, the right end of the main valve core is connected with the first connecting rod in a matched mode through a first universal coupling, the right end of the first connecting rod is connected with the first valve seat in a matched mode, and a first reset spring is sleeved between the right end of the main valve core and the first valve seat; a rotary-push small valve is arranged in a casing II below the main valve core in a matching manner, a check valve which is conducted from left to right is arranged in the rotary-push small valve, a high-pressure leading port, a flow passage plugging port, a rotary-spraying flow passage, a rotary-spraying plugging port and a small valve rotary nozzle are arranged on the rotary-push small valve on the right side of the check valve, a rotary-spraying leading port and a small valve rotary nozzle which are communicated with the rotary-spraying flow passage are correspondingly arranged on the wall of the rotary-push small valve, a low-pressure leading port and a pressure compensation leading port are arranged on the rotary-push small valve on the left side of the check valve, a secondary valve cavity is arranged on the left; the secondary valve cavity is connected with a valve sleeve through hole arranged on the valve sleeve through a plugging flow channel arranged on the second shell and is communicated with the main valve cavity and the rotary disc cavity; the right side of the small rotary push valve is in fit connection with a second connecting rod through a second universal coupling, the right end of the second connecting rod is in fit connection with a second valve seat, a second return spring is sleeved between the right end of the small rotary push valve and the second valve seat, when the small rotary push valve moves rightwards, the high-pressure guide port is communicated with the high-pressure cavity, and when the small rotary push valve moves leftwards, the low-pressure guide port is communicated with the second oil return cavity; the small valve rotary nozzle sprays hydraulic oil to drive the rotary push small valve to rotate; the first cam is in top contact fit with the right end of the first connecting rod, and the second cam is in top contact fit with the right end of the second connecting rod;
the clamping device comprises a clamp and a clamping plate thereof, the clamping plate is fixedly arranged at the front end of the piston rod, the rear end of the piston rod is matched with a push plate, the push plate is arranged in the piston body to divide the cavity of the piston body into a piston cavity I and a piston cavity II, and the push plate is in sealing sliding fit with the cavity of the piston body; the first piston cavity is communicated with the reversing port, and the second piston cavity is communicated with the reversing port.
The hydraulic elastic clamp device with the phase difference is characterized in that a convex column is arranged at the left end of a rotary push small valve, preferably three convex columns are arranged, a small valve rotary nozzle is arranged on the side wall of the convex column, and the spraying angle of the small valve rotary nozzle and the left end face form a-degree included angle, preferably an included angle.
The hydraulic elastic clamp device with the phase difference is characterized in that a first plugging screw is correspondingly arranged on a second shell below a plugging flow channel.
The hydraulic elastic clamp device with the phase difference is characterized in that three rotary nozzles communicated with a rotary disc cavity are uniformly distributed on a rotary disc.
The hydraulic elastic clamp device with the phase difference is characterized in that a second blocking screw correspondingly matched with the pressure compensation cavity is arranged on a second shell above the pressure compensation cavity.
The hydraulic elastic clamp device with the phase difference is characterized in that a bearing and a bearing seat are arranged on the left side of the rotating disc in a matched mode, a spring seat is correspondingly arranged on the inner side of the shell, a spring is arranged between the spring seat and the bearing seat in a matched mode, and a jacking position screw matched with the spring seat in an elastic jacking mode is arranged on the left side of the spring seat.
The hydraulic elastic clamp device with the phase difference is characterized in that a first cam and a second cam are concentric circles, and the first cam is arranged on the outer ring of the second cam and forms the phase difference when rotating synchronously; two sections of concentric arcs with equal included angles are oppositely arranged on the first cam and the second cam, and transition curves of the two sections of concentric arcs of the first cam and the second cam are Archimedes constant speed curves.
The hydraulic elastic clamp device with the phase difference is characterized in that a cam shell is arranged outside the first cam and the second cam in a matched mode.
According to the technical scheme of the phase difference hydraulic elastic clamp device, the handle is pushed, the first cam is arranged on the outer ring of the second cam, a phase difference is formed during synchronous rotation, when the device runs, the small rotary push valve is opened firstly, the main valve core is opened later, the small rotary push valve is moved rightwards firstly, the high-pressure guide port is communicated with the high-pressure cavity, the low-pressure guide port and the pressure compensation guide port are communicated with the pressure compensation cavity, the right H cavity communicated with the pressure compensation cavity is high-pressure oil, and leftward thrust is also provided for the main valve core, so that labor is saved when the handle is pushed manually; the main valve core can be pushed leftwards and rightwards, and can also rotate under the driving of the rotating disk, and the rotary push small valve can also rotate under the action of hydraulic oil sprayed from the rotary nozzle, so that the main valve core and the rotary push small valve cannot be clamped, the viscous resistance is reduced, the handle is pulled by hand easily and labor-saving, and the working efficiency is obviously improved; under the combined action of the main valve core and the rotary push small valve, the invention obviously reduces the labor intensity and improves the working efficiency. Because the edges of the first cam and the second cam are provided with the stable pressure-retaining area of the port A and the stable pressure-retaining area of the port B which have the same structure, the reversing valve is switched to the reversing port A to be kept for a period of time, and then switched to the reversing port B to be kept for a period of time; when the piston is reversed to the reversing port A, hydraulic oil enters the piston cavity II, the push plate moves leftwards, and the clamping plate is loosened; when the direction is changed to the direction changing port B, hydraulic oil enters the piston cavity I, the push plate moves rightwards, and the clamping plate is clamped; the use is simple and convenient.
Drawings
FIG. 1 is a schematic structural view of the present invention;
FIG. 2 is a partial schematic view of the present invention;
FIG. 3 is a schematic structural diagram of a first cam and a second cam according to the present invention;
FIG. 4 is a schematic structural view of a main spool of the present invention;
fig. 5 is a schematic structural view of the valve sleeve of the present invention;
fig. 6 is a schematic structural view of the reversing valve sleeve of the present invention;
FIG. 7 is a schematic perspective view of a main valve element of the present invention;
FIG. 8 is a schematic view of a rotary push valve according to the present invention;
FIG. 9 is a schematic structural view of the left end face of the rotary push small valve of the present invention;
in the figure: 1-first shell, 2-oil return cavity, 3-spring seat, 4-spring, 5-bearing seat, 6-rotating disk, 601-rotating nozzle, 7-valve sleeve, 701-valve sleeve through hole, 8-second shell, 9-first return port, 10-main valve cavity through hole, 11-main valve core, 12-reversing port A, 13-reversing cavity A, 14-high pressure oil inlet, 15-reversing port B, 16-reversing valve sleeve, 17-reversing cavity B, 18-second return port, 19-second return port, 20-second blocking screw, 21-pressure compensation flow channel, 22-pressure compensation cavity, 23-third shell, 24-first valve seat, 25-first connecting rod, 26-universal coupling, 27-first return spring, 27 a-second return spring, 28-connecting rod II, 29-valve seat II, 30-right H cavity, 31-universal coupling II, 32-left H cavity, 33-pressure compensation leading port, 34-low pressure leading port, 35-rotary push small valve, 35 a-rotary spray leading port, 35 b-rotary spray flow channel, 35 c-rotary spray flow channel plug, 35 d-small valve rotary spray port, 35 e-convex column, 36-check valve, 37-high pressure cavity, 38-high pressure leading port, 39-flow channel plug, 40-screw cover, 42-secondary valve cavity, 43-oil return cavity I, 44-plug screw I, 45-plug flow channel, 46-main valve cavity, 47-rotary disk cavity, 48-bearing, 49-oil return port III, 50-top screw, 51-cam I, 52-rotating shaft, 53-cam II, 54-cam shell, 55-handle, 57-A stable pressure maintaining area, 58-B stable pressure maintaining area, 59-piston cavity I, 60-piston body, 61-piston cavity II, 62-push plate, 63-piston rod, 64-clamping plate and 65-clamp.
Detailed Description
The invention is further described below with reference to the accompanying drawings.
As shown in the figure, the phase difference hydraulic tightening clamp device comprises a handle 55 and a rotating shaft 52 which is in matched connection with the handle 55, wherein a first cam 51 and a second cam 53 are coaxially arranged on the rotating shaft 52, a phase difference is arranged between the first cam 51 and the second cam 53, and a stable pressure-retaining area 57 at an opening A and a stable pressure-retaining area 58 at an opening B are synchronously arranged on the first cam 51 and the second cam 53;
the reversing valve is characterized by further comprising a reversing valve body formed by connecting a first shell 1, a second shell 8 and a third shell 23 in a matched mode, wherein an oil return cavity 2 and a third return port 49 are arranged in the first shell 1, a main valve core 11 is arranged in the second shell 8, a reversing valve sleeve 16 is arranged in the middle of the main valve core 11 in a matched mode, a first oil return cavity 43, a reversing cavity A13, a high pressure cavity 37, a reversing cavity B17, a second oil return cavity 19, a left H cavity 32, a pressure compensation cavity 22 and a right H cavity 30 are formed between the main valve core 11 and the reversing valve sleeve 16 and the second shell 8, and a first return port 9, a reversing port A12, a high-pressure oil inlet 14, a reversing port B15 and a second return port 18 are correspondingly arranged; when the main valve core 11 moves rightwards, the first oil return cavity 43 is communicated with the reversing cavity A13; when the main valve core 11 moves leftwards, the oil return cavity II 19 is communicated with the reversing cavity B17; the oil return cavity II 19 is communicated with the left H cavity 32, the pressure compensation cavity 22 is communicated with the right H cavity 30, and the oil return cavity II 19 is communicated with the pressure compensation cavity 22 through a pressure compensation flow passage 21. the rotary valve is characterized in that the left end of the main valve element 11 is tightly matched with a rotary disk 6, the rotary disk 6 is installed in the oil return cavity 2, a main valve cavity 46 of the main valve element 11 is communicated with a rotary disk cavity 47 of the rotary disk 6, a rotary nozzle 601 communicated with the rotary disk cavity 47 is arranged on the rotary disk 6, a valve sleeve 7 is arranged between the main valve element 11, a shell I1 and a shell II 8 in a matching way, the right end of the main valve element 11 is connected with a connecting rod I25 in a matching way through a universal coupling I26, the right end of the connecting rod I25 is connected with a valve seat; a rotary-push small valve 35 is arranged in a matching manner in a second shell 8 below the main valve core 11, a check valve 36 which is communicated from left to right is arranged in the rotary-push small valve 35, a high-pressure guide port 38, a flow channel blockage 39, a rotary-spraying flow channel 35b, a rotary-spraying blockage 35c and a small-valve rotary-spraying port 35d are arranged on the rotary-push small valve 35 on the right side of the check valve 36, a rotary-spraying guide port 35a and a small-valve rotary-spraying port 35d which are communicated with the rotary-spraying flow channel 35b are correspondingly arranged on the pipe wall of the rotary-push small valve 35, a low-pressure guide port 34 and a pressure compensation guide port 33 are arranged on the rotary-push small valve 35 on the left side of the check valve 36, a secondary valve cavity 42 is arranged on the left side of; the secondary valve cavity 42 is connected with a valve sleeve through hole 701 arranged on the valve sleeve 7 through a blocking flow channel 45 arranged on the second shell 8 and then is communicated with the main valve cavity 46 and the rotary disk cavity 47; the right side of the small rotary push valve 35 is connected with a second connecting rod 28 in a matched mode through a second universal coupling 31a, the right end of the second connecting rod 28 is connected with a second valve seat 29 in a matched mode, a second return spring 27a is sleeved between the right end of the small rotary push valve 35 and the second valve seat 29, when the small rotary push valve 35 moves rightwards, the high-pressure guide port 38 is communicated with the high-pressure cavity 37, and when the small rotary push valve 35 moves leftwards, the low-pressure guide port 34 is communicated with the second oil return cavity 19; the small valve rotary nozzle 35d injects hydraulic oil to drive the rotary push small valve 35 to rotate; the first cam 51 is in top contact fit with the right end of the first connecting rod 25, and the second cam 53 is in top contact fit with the right end of the second connecting rod 28;
the clamping device comprises a clamp 65 and a clamping plate 64 thereof, the clamping plate 64 is fixedly arranged at the front end of a piston rod 63, a push plate 62 is arranged at the rear end of the piston rod 63 in a matching manner, the push plate 62 is arranged in the piston body 60 to divide the cavity of the piston body into a first piston cavity 59 and a second piston cavity 61, and the push plate 62 is in sealing sliding fit with the cavity of the piston body 60; the first piston chamber 59 communicates with the reversing port B15 and the second piston chamber 61 communicates with the reversing port A12.
Further, a driving mechanism in which the rotating shaft 52 is engaged with and connected to the driving mechanism is constituted by a motor and a speed reducer 55, and the rotating shaft 52 is fixedly connected to an output shaft of the speed reducer 55.
Furthermore, the left end of the small rotary push valve 35 is provided with 2-5 convex columns 35e, preferably three convex columns 35e, the small rotary valve nozzle 35d is arranged on the side wall of the convex column 35e, the spraying angle of the small rotary valve nozzle 35d and the left end face form an included angle of 20-40 degrees, preferably 30 degrees, and the structure is arranged, so that the small rotary push valve 35 can rotate more easily.
Furthermore, a first plugging screw 44 and a screw cover 40 are correspondingly arranged on the second shell 8 below the first plugging flow channel 45, and the flow of high-pressure oil in the first plugging flow channel 45 can be adjusted by adjusting the size of a gap between the first plugging screw 44 and the first plugging flow channel 45, so that the rotation speed of a main valve is adjusted.
Furthermore, three rotary nozzles 601 communicated with the rotary disc cavity 47 are uniformly distributed on the rotary disc 6, and the three rotary nozzles 601 laterally spray high-pressure oil to drive the rotary disc 6 to rotate.
Further, a second blocking screw 20 correspondingly matched with the pressure compensation cavity 22 is arranged on the second shell 8 above the pressure compensation cavity 22, and in the reversing process, the pressure compensation cavity 22 is in a high-pressure stage, and the pressure relief time is adjusted by adjusting a gap between the second blocking screw 20 and the pressure compensation flow channel 21.
Further, the left side of the rotating disc 6 is provided with a bearing 48 and a bearing seat 5 in a matching manner, the inner side of the first shell 1 is correspondingly provided with a spring seat 3, a spring 4 is arranged between the spring seat 3 and the bearing seat 5 in a matching manner, and the left side of the spring seat 3 is provided with a top position screw 50 which is in contact fit with the elastic top of the spring seat. This structure setting not only can be through the elasticity size of adjusting the position adjustment rotary disk 6 right of top position screw 50, can also make rotary disk 6 steadily rotate, and stability is better.
Further, the first cam 51 and the second cam 53 are concentric circles, and the first cam 51 forms a phase difference when rotating synchronously on the outer ring of the second cam 53; two concentric arcs with the same included angle are oppositely arranged on the first cam 51 and the second cam 53, and transition curves of the two concentric arcs of the first cam 51 and the second cam 53 both adopt Archimedes constant speed curves. The first cam 51 and the second cam form a phase difference when rotating synchronously, and when in operation, the small valve 35 can be pushed to open firstly, and the main valve element 11 is opened later.
Further, the cam housing 54 is externally provided on the first cam 51 and the second cam 53 in a matching manner.
When the hydraulic valve is used, the handle 55 is pushed, the first cam 51 is arranged on the outer ring of the second cam 53, a phase difference is formed during synchronous rotation, during operation, the first rotary push small valve 35 is opened, the main valve element 11 is opened, the first rotary push small valve 35 moves rightwards, the high-pressure guide port 38 is communicated with the high-pressure cavity 37, the low-pressure guide port 34 and the pressure compensation guide port 33 are communicated with the pressure compensation cavity 22, and the right H cavity 30 communicated with the pressure compensation cavity 22 forms a high-pressure oil cavity to provide leftward thrust for the main valve element 11; meanwhile, high-pressure oil passes through the small valve rotary nozzle 35d, the secondary valve cavity 42, the blocking flow channel 45, the main valve cavity 46 and the rotary disk cavity 47 and is finally sprayed out from the rotary nozzle 601 on the rotary disk 6, the rotary disk 6 rotates to drive the main valve core 11 which is tightly matched and connected with the rotary disk to rotate together, the main valve core 11 cannot be clamped, the viscous resistance is reduced, and the main valve core 11 is always in a rotating state in an opening state. And the small valve 35 can be rotated under the action of hydraulic oil sprayed from the small valve rotary nozzle 35d, so that the small valve 35 can not be clamped, the viscous resistance is reduced, the abrasion is not easy to occur, and the labor is obviously saved when the handle is pulled by hands. Under the combined action of the main valve element 11 and the rotary push small valve 35, the invention obviously reduces the labor intensity and improves the working efficiency.
Because the edges of the first cam 51 and the second cam 53 are provided with the stable pressure-retaining area 57 of the port A and the stable pressure-retaining area 58 of the port B which have the same structure, the reversing valve is switched to the reversing port A12 to be kept for a period of time, and then switched to the reversing port B15 to be kept for a period of time; when the direction is changed to the direction changing port A12, hydraulic oil enters the second piston cavity 61, the push plate 62 moves leftwards, and the clamping plate 64 is loosened; when the direction is changed to a direction changing port B15, hydraulic oil enters the first piston cavity 59, the push plate 62 moves rightwards, and the clamping plate 64 is clamped; the use is simple and convenient.
Claims (8)
1. A phase difference hydraulic elastic clamp device is characterized by comprising a handle (55) and a rotating shaft (52) which is connected with the handle in a matched mode, wherein a first cam (51) and a second cam (53) are coaxially arranged on the rotating shaft (52), a phase difference is arranged between the first cam (51) and the second cam (53), and a stable pressure maintaining area (57) at an opening A and a stable pressure maintaining area (58) at an opening B are synchronously arranged on the first cam (51) and the second cam (53);
the reversing valve is characterized by further comprising a reversing valve body formed by connecting a first shell (1), a second shell (8) and a third shell (23) in a matched mode, an oil return cavity (2) and a third return port (49) are arranged in the first shell (1), a main valve core (11) is arranged in the second shell (8), a reversing valve sleeve (16) is arranged in the middle of the main valve core (11) in a matched mode, a first return cavity (43), a reversing cavity A (13), a high pressure cavity (37), a reversing cavity B (17), a second return cavity (19), a left H cavity (32), a pressure compensation cavity (22) and a right H cavity (30) are formed between the main valve core (11) and the reversing valve sleeve (16) and the second shell (8), and a first return port (9), a reversing port A (12), a high-pressure oil inlet (14), a reversing port B (15) and a second return port (18) are correspondingly; when the main valve core (11) moves rightwards, the first oil return cavity (43) is communicated with the reversing cavity A (13); when the main valve core (11) moves leftwards, the oil return cavity II (19) is communicated with the reversing cavity B (17); the oil return cavity II (19) is communicated with the left H cavity (32), the pressure compensation cavity (22) is communicated with the right H cavity (30), the oil return cavity II (19) is communicated with the pressure compensation cavity (22) through a pressure compensation flow passage (21), the rotating disc (6) is tightly arranged at the left end of the main valve core (11), the rotating disc (6) is arranged in the oil return cavity (2), a main valve cavity (46) of a main valve core (11) is communicated with a rotating disc cavity (47) of a rotating disc (6), a rotating nozzle (601) communicated with the rotating disc cavity (47) is arranged on the rotating disc (6), a valve sleeve (7) is arranged between the main valve core (11) and a first shell (1) and a second shell (8) in a matching mode, the right end of the main valve core (11) is connected with a first connecting rod (25) in a matching mode through a first universal coupling (26), the right end of the first connecting rod (25) is connected with a first valve seat (24) in a matching mode, and a first reset spring (27) is arranged between the right end of the main valve core (11) and the first valve seat; a rotary-push small valve (35) is arranged in a second shell (8) below the main valve core (11) in a matching manner, a check valve (36) which is communicated from left to right is arranged in the rotary-push small valve (35), a high-pressure guide port (38), a flow channel blocking port (39), a rotary-spraying flow channel (35 b), a rotary-spraying blocking port (35 c) and a small-valve rotary-spraying port (35 d) are arranged on the rotary-push small valve (35) on the right side of the check valve (36), a rotary-spraying guide port (35 a) and a small-valve rotary-spraying port (35 d) which are communicated with the rotary-spraying flow channel (35 b) are correspondingly arranged on the pipe wall of the rotary-push small valve (35), a low-pressure guide port (34) and a pressure compensation guide port (33) are arranged on the rotary-push small valve (35) on the left side, a secondary valve cavity (42) is communicated with the rotary-spraying flow channel (35 b) through the; the secondary valve cavity (42) is connected with a valve sleeve through hole (701) arranged on the valve sleeve (7) through a plugging flow channel (45) arranged on the second shell (8), and then is communicated with the main valve cavity (46) and the rotating disc cavity (47); the right side of the small rotary push valve (35) is connected with a second connecting rod (28) in a matched mode through a second universal coupling (31 a), the right end of the second connecting rod (28) is connected with a second valve seat (29) in a matched mode, a second return spring (27 a) is sleeved between the right end of the small rotary push valve (35) and the second valve seat (29), when the small rotary push valve (35) moves rightwards, the high-pressure guide port (38) is communicated with the high-pressure cavity (37), and when the small rotary push valve (35) moves leftwards, the low-pressure guide port (34) is communicated with the second oil return cavity (19); the small valve rotary nozzle (35 d) injects hydraulic oil to drive the rotary push small valve (35) to rotate; the cam I (51) is in top contact fit with the right end of the connecting rod I (25), and the cam II (53) is in top contact fit with the right end of the connecting rod II (28);
the clamping device comprises a clamp (65) and a clamping plate (64) of the clamp, the clamping plate (64) is fixedly arranged at the front end of a piston rod (63), the rear end of the piston rod (63) is provided with a push plate (62) in a matching manner, the push plate (62) is arranged in a piston body (60) to divide the cavity of the piston body into a first piston cavity (59) and a second piston cavity (61), and the push plate (62) is in sealing sliding fit with the cavity of the piston body (60); the first piston cavity (59) is communicated with the reversing port B (15), and the second piston cavity (61) is communicated with the reversing port A (12).
2. A phase difference hydraulic elastic clamp device according to claim 1, wherein 2-5 convex columns (35 e) are arranged at the left end of the rotary push small valve (35), the small valve rotary nozzle (35 d) is arranged on the side wall of the convex column (35 e), and the injection angle of the small valve rotary nozzle (35 d) forms an included angle of 20-40 degrees with the left end surface.
3. A phase difference hydraulic elastic clamp device according to claim 1, wherein a first blocking screw (44) is correspondingly arranged on the second shell (8) below the blocking flow passage (45).
4. A phase difference hydraulic tensioning clamp device according to claim 1, characterized in that three spinning nozzles (601) are uniformly arranged on the rotating disc (6) and communicate with the rotating disc chamber (47).
5. A phase difference hydraulic elastic clamp device according to claim 1, wherein a second blocking screw (20) correspondingly matched with the pressure compensation chamber (22) is arranged on the second housing (8) above the pressure compensation chamber (22).
6. A phase difference hydraulic elastic clamp device according to claim 1, wherein a bearing (48) and a bearing seat (5) are arranged on the left side of the rotating disc (6) in a matching manner, a spring seat (3) is correspondingly arranged on the inner side of the first casing (1), a spring (4) is arranged between the spring seat (3) and the bearing seat (5) in a matching manner, and a jacking screw (50) which is in contact fit with the spring seat (3) in a resilient jacking manner is arranged on the left side of the spring seat (3).
7. A phase difference hydraulic tensioning clamp device according to claim 1 wherein the first cam (51) and the second cam (53) are concentric, the first cam (51) being on the outer race of the second cam (53) and rotating synchronously to provide the phase difference; two concentric arcs with the same included angle are oppositely arranged on the first cam (51) and the second cam (53), and transition curves of the two concentric arcs of the first cam (51) and the second cam (53) adopt Archimedes constant speed curves.
8. A phase difference hydraulic elastic clamp device according to claim 1, wherein the cam housing (54) is externally fitted to the cam one (51) and the cam two (53).
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| CN113600117B (en) * | 2021-09-30 | 2021-12-14 | 东营科宏化工有限公司 | Reaction kettle for producing p-tert-butylcyclohexyl acetate and using method thereof |
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| KR0129620B1 (en) * | 1995-02-28 | 1998-04-10 | 김태구 | Assembly for transferring jig |
| JPH10185787A (en) * | 1996-12-26 | 1998-07-14 | Toyota Central Res & Dev Lab Inc | Fatigue test device |
| CN103753448B (en) * | 2013-12-30 | 2015-05-27 | 中国建材检验认证集团苏州有限公司 | Lever-type pneumatic clamp |
| CN105965424A (en) * | 2016-06-22 | 2016-09-28 | 陕西宝成航空仪表有限责任公司 | Pneumatic combined clamp for assembling of throttle valve assemblies |
| CN106286885A (en) * | 2016-08-30 | 2017-01-04 | 宁波长壁流体动力科技有限公司 | A kind of main valve plug for reversal valve |
| CN106930994B (en) * | 2017-05-09 | 2018-03-09 | 江苏力源液压机械有限公司 | Position floating reversal valve is jumped in the manual pressurize of tractor |
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Effective date of registration: 20211203 Address after: 318000 No. 577, Jingshan village, fengjiang street, Luqiao District, Taizhou City, Zhejiang Province Patentee after: Frank lubrication technology (Taizhou) Co.,Ltd. Address before: 310018 No. 2 street, Xiasha Higher Education Zone, Hangzhou, Zhejiang Patentee before: HANGZHOU DIANZI University |
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