CN103452940B - Integrated valve block - Google Patents
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- CN103452940B CN103452940B CN201310443710.7A CN201310443710A CN103452940B CN 103452940 B CN103452940 B CN 103452940B CN 201310443710 A CN201310443710 A CN 201310443710A CN 103452940 B CN103452940 B CN 103452940B
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Abstract
The invention discloses an integrated valve block and belongs to the field of hydraulic technology. The integrated valve block comprises a valve body (200) provided with an inner cavity (201). Through holes are formed at two ends of the inner cavity (201) of the valve body (200). Five annular through holes are radially formed between the outer wall face of the valve body (200) and the inner cavity. A valve element (220) is nested into the inner cavity (201). Four coaxial cylinders with the same cross section are disposed at intervals in the axial direction of the valve element (220). The four cylinders of the valve element (220) are matched with the inner cavity (201) to form a zero-openness two-position four-way reversing valve. Compared with the prior art, the integrated valve block is free of an electric control system and simple in system.
Description
Technical field
The invention belongs to hydraulics field, relate to a kind of supercharging device, relate in particular to a kind of pressurized cylinder, integrated valve block and supercharging device thereof.
Background technique
Pressurized cylinder principle on common meaning is according to the different hydraulic oil scaling up output that makes input of the useful area of piston and plunger.Pressure ratio equals the inverse ratio of big or small piston area.This pressurized cylinder only carries out one-level supercharging conversion, and pressure ratio is the once linear proportionate relationship of piston and plunger radial area, and the spatial volume that does not make full use of pressurized cylinder carries out supercharging.In order to realize two-way continuous supercharging, there is following Double-action reciprocating formula pressurized machine, such as solenoid directional control valve etc.But solenoid directional control valve complex structure, is easily out of order.For this reason, name is called " a kind of Double-effect reciprocating hydraulic pressure booster ", the patent No. is that 201120363620.3 Chinese utility model patent discloses a kind of pressurized machine, its technical problem that will solve is to provide a kind of reciprocating hydraulic booster simple in structure, its technological scheme adopting is: a kind of reciprocating hydraulic booster, comprise supercharging part and automatic reverse control valve, the top and bottom of the control spool of automatic reverse control valve are connected with respectively upper piston and lower piston, the cross-section area of upper piston is greater than the cross-section area of lower piston, the first hydraulic fluid port of automatic reverse control valve is communicated with lower low-pressure cavity, the second hydraulic fluid port is communicated with upper low-pressure cavity, return opening is communicated with drainback passage, high pressure hydraulic fluid port is communicated with high-pressure oil passage, supercharging part also has oil-feed runner, oil return runner, first is controlled runner and second and controlled runner, on the side face of low-pressure plunger, have annular connectivity slot, the first control runner and second is controlled runner and is all communicated with the upper chamber of upper piston by the first other road of connecting.The advantage of this patent is the automatic reverse by hydraulic oil pipeline structure control oil hydraulic cylinder, realizes the function of continuous wave output high pressure oil, without complicated automatical control system and sensor.Shortcoming is that, under same volume, pressure ratio is little.
Summary of the invention
For the deficiencies in the prior art, the technical problem to be solved in the present invention is, dwindles the radially area of pressurized cylinder, utilizes less spatial volume to realize larger pressure ratio.
In order to realize above-mentioned technical problem, the technical solution used in the present invention is:
A kind of pressurized cylinder, comprise first stage piston (10), second piston (20) and (30) three parts of cylinder barrel, first stage piston (10) is sleeved on the inner chamber of second piston (20), second piston (20) is sleeved on the inner chamber of cylinder barrel (30), first stage piston (10) and second piston (20) move mutually, complete the supercharging for the first time to hydraulic oil; The relative movement of second piston (20) and cylinder barrel (30) completes the supercharging for the second time to hydraulic oil.
Described first stage piston (10) comprises main body, main body is the cylindrical body (13) that a peripheral surface is provided with annular groove (12), outwards respectively there is a disk (14) at the two ends of cylindrical body (13), the area of described disk (14) is less than the cross-section area of described cylindrical body (13), and described disk (14) is fixedly connected with in the mode keeping at a certain distance away with described cylindrical body (13).
Described second piston (20) comprises main body, in the middle of main body, is a hollow circular cylinder (22) that cross-section area is larger, and the inner chamber of hollow circular cylinder (22) is used for holding the cylindrical body (13) of first stage piston (10); Cylindrical body (22) two ends outwards respectively arrange a hollow circular cylinder (23) that cross-section area is less in the mode mutually connecting, and the inner chamber of hollow circular cylinder (23) is used for holding the disk (14) of first stage piston (10); The two ends of two hollow circular cylinders (23) are outwards respectively provided with a disk (24), and the area of described disk (24) is identical with the cross-section area of described cylindrical body (23); Described disk (24) is fixedly connected with the end face non-tight formula of described hollow circular cylinder (23), between described disk (24) and the end face of described hollow circular cylinder (23), form certain gap, for fluid turnover; The outside of two disks (24) is respectively provided with a disk (25) that Area Ratio disk 24 areas are little, and described disk (25) is fixedly connected with in the mode keeping at a certain distance away with described disk (24).
The inner chamber that the main body cylindrical body (13) of described first stage piston (10) is sleeved on the mediate cylindrical (22) of described second piston (20) also can move radially in the inner chamber of cylindrical body (22), and the external diameter of cylindrical body (13) equates with the internal diameter of cylindrical body (22); The inner chamber that the integrated disc portions (14) of described first stage piston (10) is sleeved on the both sides cylindrical body (23) of described second piston (20) also can move radially in the inner chamber of cylindrical body (23), and the external diameter of disk (14) equates with the internal diameter of cylindrical body (23).
First stage piston (10) and second piston (20) move mutually, complete the supercharging for the first time to hydraulic oil.
The outer circumferential face of described second piston (20) main body mediate cylindrical (22) is outwards provided with a locating stud (26), with prevent second piston (20) in a circumferential direction relatively cylinder barrel (30) rotate.
On the wall of described cylindrical body (22) with described locating stud (26) in same in the radial direction, arrange that in described locating stud (26) bilateral symmetry two commutations control oily inside filler openings (271,272); The groove (12) of first stage piston (10) is communicated with hydraulic fluid port (271) and hydraulic fluid port (272) respectively when moving to left position or right position; With filler opening (271) on same circumference, radially angle is that the position of α=144 ° is provided with the commutation identical with filler opening (271) size and controls oily inside oil outlet (281); With filler opening (272) on same circumference, radial angle is-position of α=-144 ° is provided with the commutation identical with filler opening (272) size and controls oily inside oil outlet (282); Near cylindrical body (22) left side and described locating stud (26) radially angle be the inside grooved hydraulic fluid port (291) that the wall of ° position, β=72 is provided with turnover work fluid; Near cylindrical body (22) right side and described locating stud (26) radially angle be-wall of ° position, β=-72 is provided with the inside grooved hydraulic fluid port (292) of turnover work fluid.
So-called radially angle is exactly angle in a circumferential direction.
Described cylinder barrel (30) comprises three sections of hollow circular cylinders (31,32,33) that perforation, cross-section area successively decrease successively mutually from centre to two ends: middle cylindrical body (31) cross-section area maximum, and the inner chamber of described cylindrical body (31) is used for holding the mediate cylindrical (22) of second piston (20); The two ends of described cylindrical body (31) are communicated with the slightly little cylindrical body (32) of cross-section area, and the inner chamber of described cylindrical body (32) is used for holding the two terminal circle cylinder (23) of described second piston (20); The two ends of described cylindrical body (32) are communicated with the cylindrical body (33) of cross-section area minimum, the sealing of cylindrical body (33) outer end, and the inner chamber of described cylindrical body (33) is used for holding the outboard disc (25) of described second piston (20).
The mediate cylindrical (22) of described second piston (20) is sleeved on the inner chamber of described cylindrical body (31) and can in the inner chamber of cylindrical body (31), moves radially, and the external diameter of cylindrical body (22) equates with the internal diameter of cylindrical body (31); The two terminal circle cylinder (23) of described second piston (20) is sleeved on the inner chamber of described cylindrical body (32) and can in the inner chamber of cylindrical body (32), moves radially, the external diameter of cylindrical body (23) is less than the internal diameter of cylindrical body (32), gapped between cylindrical body (23) and cylindrical body (32) inside and outside wall, hold fluid; The outboard disc (25) of described second piston (20) is sleeved on the inner chamber of described cylindrical body (33) and can in the inner chamber of cylindrical body (33), moves radially, and disk (25) external diameter equates with cylindrical body (33) internal diameter.
The relative movement of second piston (20) and cylinder barrel (30) completes the supercharging for the second time to hydraulic oil.The oil pocket that high pressure oil forms from the exterior edge face of the disk (25) of described second piston (20) and cylindrical body (33) inwall of described cylinder barrel (30) is for the second time exported along moving direction.
The internal surface of the mediate cylindrical (31) of described cylinder barrel (30) is provided with a rectangular recess (34) arranging vertically, there is a manhole (340) that connects exterior line the intermediate portion of this groove (34), and manhole (340) is that oily outside filler opening is controlled in commutation; The locating stud (26) of second piston (20) inserts in described manhole (340), prevents that second piston (20) from rotating; Described rectangular recess (34) and the commutation of second piston (20) are controlled oily inside filler opening (271) and commutation and are controlled oily inside filler opening (272) and be communicated with, the power oil that provides change-over valve core to move for external control devices.
Described cylindrical body (31) the down either side of through hole (340), with the radially angle of through hole (340) be α=144 ° and-cylindrical inner surface of α=-144 ° is provided with two rectangular recess, two rectangular recess are respectively equipped with a manhole (351,352) that connects exterior line, and this is that oily outside oil outlet is controlled in commutation; Described manhole (351) coordinates with the oil outlet (281) of second piston (20); Described manhole (352) coordinates with the oil outlet (282) of second piston (20), the power oil moving to external control devices output change-over valve core; With the radially angle of described through hole (340) be β=72 ° and-cylindrical inner surface of β=-72 ° direction is provided with two grooves, described two grooves are respectively equipped with a manhole (361,362) that connects exterior line, and this is the outside hydraulic fluid port of turnover work fluid; Manhole (361) coordinates with the hydraulic fluid port (291) of second piston (20); Manhole (362) is used in conjunction with the hydraulic fluid port (292) of second piston (20), for the pressurization for the first time of this pressurized cylinder provides pressure oil.
The top of two cylindrical bodys (33) exterior edge face at described cylinder barrel (30) two ends sets out respectively hydraulic fluid port: the hydraulic fluid port (372) on the hydraulic fluid port (371) on left end cylindrical body (33) top and right-hand member cylindrical body (33) top, they are supercharging oil outlets for the second time, for exporting the high pressure oil after secondary booster; Filler opening (381,382) is offered respectively in the bottom of two cylindrical bodys (33) exterior edge face at described cylinder barrel (30) two ends: the hydraulic fluid port (382) of the hydraulic fluid port (381) of left end cylindrical body (33) bottom and right-hand member cylindrical body (33) bottom, they are supercharging filler openings for the second time, for supercharging for the second time provides fluid.
The bottom, outer end of the cylindrical body (32) of described cylinder barrel (30) left and right sides arranges respectively leakage compensation hydraulic fluid port: the compensation hydraulic fluid port (391) in left side and the compensation hydraulic fluid port (392) on right side.
Preferred scheme is, the height of cylindrical body (13) is greater than two times of distance between hydraulic fluid port (271) and hydraulic fluid port (272).
Preferred scheme is that the height of cylindrical body (22) is greater than 1.5 times of cylindrical body (13) height.
Preferred scheme is, grooved hydraulic fluid port (291) and grooved hydraulic fluid port (292) are positioned at the two ends of cylindrical body (22), and length equals the height of the cylindrical body (22) of 1/3 times.
The integrated valve block that a kind of and above-mentioned pressurized cylinder is used in conjunction with, described integrated valve block comprises valve body (200), valve body (200) is provided with inner chamber (201), described valve body (200) is offered respectively through hole in inner chamber (201) end positions: PATENT left side via (202) and right side through hole (203), PATENT left side via (202) and right side through hole (203) are communicated with respectively other hydraulic fluid ports, described valve body (200) outer wall wall is to five annular through-holes are radially set between inner chamber simultaneously, from left to right be followed successively by: through hole (204), through hole (205), through hole (206), through hole (207), through hole (208), inner chamber (201) inner sleeve cartridge spool (220), described spool (220) arranges four coaxial prismatic cylindrical bodys in the mode keeping at a certain distance away on its axial direction: cylindrical body (221), cylindrical body (222), cylindrical body (223) and cylindrical body (224), and four cylindrical bodys of described spool (200) and described inner chamber (201) coordinate the two-position four way change valve that becomes zero aperture, described valve body (200) is provided with hydraulic fluid port T, hydraulic fluid port T1, hydraulic fluid port T2, hydraulic fluid port P, hydraulic fluid port P0, hydraulic fluid port A, hydraulic fluid port B, hydraulic fluid port K1, hydraulic fluid port K2, also comprises Pilot operated check valve M, Pilot operated check valve N, Pilot operated check valve E1 and Pilot operated check valve E2.
Described Pilot operated check valve M comprises that two inner hydraulic fluid port M1, M2 are connected outside hydraulic fluid port M3 with one, inner hydraulic fluid port M1 is communicated with inner chamber (201), inner hydraulic fluid port M2 is communicated with through hole (205) and outside hydraulic fluid port A on valve body, outside hydraulic fluid port M3 is communicated with the outside oil circuit of integrated valve block, is communicated with the compensation hydraulic fluid port (391) of above-mentioned pressurized cylinder.
Described Pilot operated check valve N comprises that two inner hydraulic fluid port N1, N2 are connected outside hydraulic fluid port N3 with one, inner hydraulic fluid port N1 is communicated with inner chamber (201), inner hydraulic fluid port N2 is communicated with through hole on valve body (207) and outside hydraulic fluid port B, hydraulic fluid port N3 is communicated with the outside oil circuit of integrated valve block, is communicated with the compensation hydraulic fluid port (392) of above-mentioned pressurized cylinder.
Described Pilot operated check valve E1 comprises three inner hydraulic fluid port E10, E11, E12, in E11, is wherein control fluid, is work fluid in E10 and E12; Hydraulic fluid port E10 is communicated with body cavity PATENT left side via (202) and hydraulic fluid port K1, and hydraulic fluid port E12 is communicated with through hole on valve body (204) and hydraulic fluid port T1, and hydraulic fluid port E11 is communicated with hydraulic fluid port K2.
Described Pilot operated check valve E2 comprises that wherein E21 is for controlling fluid for three inner hydraulic fluid port E20, E21, E22(, and E20, E22 are work fluid); Hydraulic fluid port E20 is communicated with body cavity right side through hole (203), and hydraulic fluid port E22 is communicated with through hole on valve body (208) and hydraulic fluid port T2, and hydraulic fluid port E21 is communicated with hydraulic fluid port K1.
Hydraulic fluid port P has external screw-thread connection mouth, communicates with the pressure oil of external hydraulic system, and hydraulic fluid port P is communicated with valve hole (206) inner, keeps being communicated with hydraulic fluid port P0 by looping pit radially simultaneously.
The hydraulic fluid port P0 mouth that is threaded in outside, is connected with external pressurization cylinder system, is connected with the manhole (340) on above-mentioned cylinder barrel (30).
Hydraulic fluid port A is provided at an outer portion with the mouth that is threaded, and is connected with external pressurization cylinder system, is communicated with the manhole (361) on above-mentioned pressurized cylinder; Hydraulic fluid port A is communicated with valve hole (205) inner, is also communicated with hydraulic fluid port M2 simultaneously.
Hydraulic fluid port B is provided at an outer portion with the mouth that is threaded, and is connected with external pressurization cylinder system, is communicated with the manhole (362) on above-mentioned pressurized cylinder; Hydraulic fluid port B is communicated with valve hole (207) inner, is also communicated with hydraulic fluid port N2 simultaneously.
Hydraulic fluid port K1 is provided at an outer portion with the mouth that is threaded, and is connected with external pressurization cylinder system, is communicated with the manhole (352) of above-mentioned pressurized cylinder; Hydraulic fluid port K1 is communicated with PATENT left side via (202) inner, is also communicated with hydraulic fluid port E10, is also communicated with hydraulic fluid port E21.
Hydraulic fluid port K2 is provided at an outer portion with the mouth that is threaded, and is connected with external pressurization cylinder system, is communicated with the manhole (351) of pressurized cylinder; Hydraulic fluid port K2 is communicated with right side through hole (203) inner, is also communicated with hydraulic fluid port E20, is also communicated with hydraulic fluid port E11.
Hydraulic fluid port T outside is provided with the mouth that is threaded, and is connected with the fuel tank of external hydraulic system; In inside, hydraulic fluid port T is communicated with E12 and E22; Hydraulic fluid port T is communicated with hydraulic fluid port T1 by one-way valve, is communicated with hydraulic fluid port T2 by one-way valve; Hydraulic fluid port T1, T2 are equipped with external screw-thread connection mouth, are connected with external pressurization cylinder system, and wherein hydraulic fluid port T1 is communicated with the oil outlet (381) of above-mentioned pressurized cylinder; Hydraulic fluid port T2 is communicated with the oil outlet (382) of above-mentioned pressurized cylinder.
Hydraulic fluid port T communicates with valve hole (204) and valve hole (208).
A kind of pressurization system, comprise above-mentioned pressurized cylinder and above-mentioned integrated valve block, described integrated valve block is connected by pipeline with described pressurized cylinder, its annexation is: the hydraulic fluid port A of integrated valve block is communicated with the manhole (361) of pressurized cylinder, the hydraulic fluid port B of integrated valve block is communicated with the manhole (362) of pressurized cylinder, for supercharging for the first time provides work fluid; The hydraulic fluid port P0 of integrated valve block is communicated with the manhole (340) of pressurized cylinder, for external control devices provides the spool power oil of selector valve; The hydraulic fluid port K1 of integrated valve block is communicated with the manhole (352) of pressurized cylinder, and the hydraulic fluid port K2 of integrated valve block is communicated with the manhole (351) of pressurized cylinder, the direction of action of the spool (220) of control integration valve piece; The hydraulic fluid port T1 of integrated valve block is communicated with the oil outlet (381) of pressurized cylinder, and the hydraulic fluid port T2 of integrated valve block is communicated with the oil outlet (382) of pressurized cylinder, is the secondary booster repairing of pressurized cylinder; On integrated valve block, the hydraulic fluid port M3 of Pilot operated check valve M is communicated with the compensation hydraulic fluid port (391) of pressurized cylinder, and on integrated valve block, the hydraulic fluid port N3 of Pilot operated check valve N is communicated with the compensation hydraulic fluid port (392) of pressurized cylinder, for pressurized cylinder supplements the fluid lacking because of leakage; The hydraulic fluid port T of integrated valve block is connected with the fuel tank of external hydraulic system; Hydraulic fluid port P has external screw-thread connection mouth, is connected with the power high pressure oil of external hydraulic system.
Compared with the pressurized cylinder of prior art, pressurized cylinder volume provided by the invention is little, especially radially volume reduces greatly, compact structure, in the pressurized cylinder of identical supercharging ratio, can realize volume and minimize, or can say in the pressurized cylinder of same volume, pressurized cylinder provided by the invention can reach larger supercharging ratio.Piston automatic reverse in running pressurized cylinder, output fluid is continuous.Do not have automatical control system to participate in, system is simple, is applicable to being applied to engineering reality.
Brief description of the drawings
Fig. 1 is pressurized cylinder structural representation of the present invention;
Fig. 2 is first stage piston structural representation;
Fig. 3 is second piston structural representation;
Fig. 4 is that hydraulic fluid port distribution schematic diagram is looked on the right side of second piston shown in Fig. 3;
Fig. 5 is the structural representation of cylinder barrel;
Fig. 6 is that hydraulic fluid port distribution schematic diagram is looked on the right side of cylinder barrel shown in Fig. 5;
Fig. 7 is the sectional structure schematic diagram of integrated valve block;
Fig. 8 is the structural representation of integrated valve block;
Fig. 9 is the hydraulic fluid port distribution floor map of integrated valve block;
Figure 10 is pressurized cylinder and integrated valve block annexation structural representation.
Embodiment
Below in conjunction with accompanying drawing, the invention is made to detailed description.
As shown in Figure 1, a kind of pressurized cylinder, comprise first stage piston 10, second piston 20 and 30 3 parts of cylinder barrel, first stage piston 10 is sleeved on the inner chamber of second piston 20, second piston 20 is sleeved on the inner chamber of cylinder barrel 30, first stage piston 10 and second piston 20 move mutually, complete the supercharging for the first time to hydraulic oil; The relative movement of second piston 20 and cylinder barrel 30 completes the supercharging for the second time to hydraulic oil.
As shown in Figure 2, described first stage piston 10 comprises main body, and main body is the cylindrical body 13 that a peripheral surface is provided with annular groove 12, and outwards respectively there are a disk 14, the area A of described disk 14 in the two ends of cylindrical body 13
14be less than the cross-sectional area A of described cylindrical body 13
13, i.e. A
14﹤ A
13; Described disk 14 is fixedly connected with in the mode keeping at a certain distance away with described cylindrical body 13, can be for example as shown in Figure 2 in the middle of disk 14 and cylindrical body 13 are welded together with a tiny cylindrical body.
As shown in Figure 3, described second piston 20 comprises main body, in the middle of main body, is a hollow circular cylinder 22 that cross-section area is larger, and the inner chamber of hollow circular cylinder 22 is for holding the main body of first stage piston 10; Cylindrical body 22 two ends outwards respectively arrange a hollow circular cylinder 23 that cross-section area is less in the mode mutually connecting, and the inner chamber of hollow circular cylinder 23 is used for holding the disk 14 of first stage piston 10; The two ends of two hollow circular cylinders 23 are outwards respectively provided with a disk 24 that area is identical with the cross-section area of cylindrical body 23, described disk 24 is fixedly connected with the end face non-tight formula of described hollow circular cylinder 23, for example, can be that the end face of cylindrical body 23 as shown in Figure 3 and the edge of disk 24 weld together by rigidity small cylinder; Between described disk 24 and the end face of described hollow circular cylinder 23, form certain gap, for fluid turnover; The outside of two disks 24 is respectively provided with a disk 25 that Area Ratio disk 24 areas are little, and described disk 25 is fixedly connected with in the mode keeping at a certain distance away with described disk 24; Its area relationship is: A
25﹤ A
24=A
23﹤ A
22.
As shown in Figure 1, the main body of described first stage piston 10 be sleeved on described second piston 20 mediate cylindrical 22 inner chamber and can in the inner chamber of cylindrical body 22, move radially; The cross-sectional area A of the main body cylindrical body 13 of first stage piston 10
13equal the inner chamber cross-sectional area A of second piston 20 mediate cylindrical 22
22, i.e. A
13=A
22; The inner chamber that disk 14 parts of described first stage piston 10 are sleeved on the both sides cylindrical body 23 of described second piston 20 also can move radially in the inner chamber of cylindrical body 23, and the area of disk 14 equals the inner chamber cross-section area of cylindrical body 23, i.e. A
14=A
23; First stage piston 10 and second piston 20 move mutually, complete the supercharging for the first time to hydraulic oil.
As shown in Figure 3, Figure 4, the outer circumferential face of described second piston 20 main body mediate cylindrical 22 is outwards provided with a locating stud 26, to prevent that second piston 20 from rotating in a circumferential direction; On the wall of described cylindrical body 22, arrange two inside filler openings that commutation control is oily in described locating stud 26 bilateral symmetry with described locating stud 26 in the radial direction in same: filler opening 271 and filler opening 272; The groove 12 of first stage piston 10 is communicated with hydraulic fluid port 271 and hydraulic fluid port 272 respectively when moving to left position or right position; With filler opening 271 on same circumference, radially angle is that the position of α=144 ° is provided with the commutation identical with filler opening 271 sizes and controls oily inside oil outlet 281; With filler opening 272 on same circumference, radial angle is-position of α=-144 ° is provided with the commutation identical with filler opening 272 sizes and controls oily inside oil outlet 282; Near cylindrical body 22 left sides and described locating stud 26 radially angle be that the wall of ° position, β=72 is provided with grooved hydraulic fluid port 291; Near cylindrical body 22 right sides and described locating stud 26 radially angle be-wall of ° position, β=-72 is provided with grooved hydraulic fluid port 292.
So-called radially angle is exactly angle in a circumferential direction.
As shown in Fig. 5 and Fig. 1, described cylinder barrel 30 comprises three sections of hollow circular cylinders that perforation, cross-section area successively decrease successively mutually from centre to two ends: cylindrical body 31, cylindrical body 32, cylindrical body 33, middle cylindrical body 31 cross-section area maximums, the inner chamber of described cylindrical body 31 is for holding the mediate cylindrical 22 of second piston 20; The two ends of described cylindrical body 31 are communicated with the slightly little cylindrical body 32 of cross-section area, and the inner chamber of described cylindrical body 32 is for holding the two terminal circle cylinder 23 of described second piston 20; The two ends of described cylindrical body 32 are communicated with the cylindrical body 33 of cross-section area minimum, cylindrical body 33 outer end sealings, and the inner chamber of described cylindrical body 33 is for holding the outboard disc 25 of described second piston 20; The mediate cylindrical 22 of described second piston 20 is sleeved on the inner chamber of described cylindrical body 31 and can in the inner chamber of cylindrical body 31, moves radially; The two terminal circle cylinder 23 of described second piston 20 is sleeved on the inner chamber of described cylindrical body 32 and can in the inner chamber of cylindrical body 32, moves radially, gapped between cylindrical body 23 and cylindrical body 32 inside and outside walls, for holding fluid; The outboard disc 25 of described second piston 20 is sleeved on the inner chamber of described cylindrical body 33 and can in the inner chamber of cylindrical body 33, moves radially, and disk 25 external diameters equate with cylindrical body 33 internal diameters; Its size relation is: A
33﹤ A
32﹤ A
31; A
31=A
22; A
33=A
25; A
23﹤ A
32.
The relative movement of second piston 20 and cylinder barrel 30 completes the supercharging for the second time to hydraulic oil.The oil pocket that high pressure oil forms from the exterior edge face of the disk 25 of described second piston 20 and cylindrical body 33 inwalls of described cylinder barrel 30 is for the second time exported along moving direction.
The internal surface of the mediate cylindrical 31 of described cylinder barrel 30 is provided with a rectangular recess 34 arranging vertically, and there is a manhole 340 that connects exterior line the intermediate portion of this groove 34, and manhole 340 is that oily outside filler opening is controlled in commutation; The locating stud 26 of second piston 20 inserts in described manhole 340, prevents that second piston 20 from rotating; Described rectangular recess 34 and the commutation of second piston 20 are controlled oily inside filler opening 271 and commutation and are controlled oily inside filler opening 272 and be communicated with, the power oil that provides change-over valve core to move for external control devices.
As shown in Figure 5 and Figure 6, described cylindrical body 31 the down either side of through hole 340, with the radially angle of through hole 340 be α=144 ° and-cylindrical inner surface of α=-144 ° is provided with two rectangular recess, two rectangular recess are respectively equipped with a manhole that connects exterior line: manhole 351 and manhole 352, and this is that oily outside oil outlet is controlled in commutation; Described manhole 351 coordinates with the oil outlet 281 of second piston 20; Described manhole 352 coordinates with the oil outlet 282 of second piston 20, the power oil moving to external control devices output change-over valve core; With the radially angle of described through hole 340 be β=72 ° and-cylindrical inner surface of β=-72 ° direction is provided with two grooves, described two grooves are respectively equipped with a manhole that connects exterior line: manhole 361 and manhole 362, and this is the outside hydraulic fluid port of turnover work fluid; Manhole 361 coordinates with the hydraulic fluid port 291 of second piston 20; Manhole 362 is used in conjunction with the hydraulic fluid port 292 of second piston 20, for the pressurization for the first time of this pressurized cylinder provides pressure oil.
The top of two cylindrical body 33 exterior edge faces at described cylinder barrel 30 two ends sets out respectively hydraulic fluid port: the hydraulic fluid port 372 on the hydraulic fluid port 371 on left end cylindrical body 33 tops and right-hand member cylindrical body 33 tops, they are supercharging oil outlets for the second time, for exporting the high pressure oil after secondary booster; Filler opening is offered respectively in the bottom of two cylindrical body 33 exterior edge faces at described cylinder barrel 30 two ends: the hydraulic fluid port 382 of the hydraulic fluid port 381 of left end cylindrical body 33 bottoms and right-hand member cylindrical body 33 bottoms, they are supercharging filler openings for the second time, for supercharging for the second time provides fluid.
The bottom, outer end of the cylindrical body 32 of described cylinder barrel 30 left and right sides arranges respectively leakage compensation hydraulic fluid port: the compensation hydraulic fluid port 391 in left side and the compensation hydraulic fluid port 392 on right side.
In order to provide oil circuit control to above-mentioned pressurized cylinder, the integrated valve block that the present invention also provides a kind of and above-mentioned pressurized cylinder to be used in conjunction with.
As shown in Figure 7, Figure 8 and Figure 9, described integrated valve block comprises valve body 200, valve body 200 is provided with inner chamber 201, and described valve body 200 is offered respectively through hole in inner chamber 201 end positions: PATENT left side via 202 and right side through hole 203, and PATENT left side via 202 and right side through hole 203 are communicated with respectively other hydraulic fluid ports; Described valve body 200 outer wall walls, to five annular through-holes are radially set between inner chamber, are from left to right followed successively by: through hole 204, through hole 205, through hole 206, through hole 207, through hole 208 simultaneously; Inner chamber 201 inner sleeve cartridge spools 220, described spool 220 arranges four coaxial prismatic cylindrical bodys in the mode keeping at a certain distance away on its axial direction: cylindrical body 221, cylindrical body 222, cylindrical body 223 and cylindrical body 224, and four cylindrical bodys of described spool 200 and described inner chamber 201 and through hole thereof coordinate the two-position four way change valve that becomes zero aperture; Described valve body 200 is provided with hydraulic fluid port T, hydraulic fluid port T1, hydraulic fluid port T2, hydraulic fluid port P, hydraulic fluid port P0, hydraulic fluid port A, hydraulic fluid port B, hydraulic fluid port K1, hydraulic fluid port K2, also comprises Pilot operated check valve M, Pilot operated check valve N, Pilot operated check valve E1 and Pilot operated check valve E2; Described Pilot operated check valve M comprises that two inner hydraulic fluid port M1, M2 are connected outside hydraulic fluid port M3 with one, inner hydraulic fluid port M1 is communicated with inner chamber 201, inner hydraulic fluid port M2 is communicated with through hole 205 and outside hydraulic fluid port A on valve body, outside hydraulic fluid port M3 is communicated with the outside oil circuit of integrated valve block, is communicated with the compensation hydraulic fluid port 391 of above-mentioned pressurized cylinder; Described Pilot operated check valve N comprises that two inner hydraulic fluid port N1, N2 are connected outside hydraulic fluid port N3 with one, inner hydraulic fluid port N1 is communicated with inner chamber 201, inner hydraulic fluid port N2 is communicated with through hole on valve body 207 and outside hydraulic fluid port B, hydraulic fluid port N3 is communicated with the outside oil circuit of integrated valve block, is communicated with the compensation hydraulic fluid port 392 of above-mentioned pressurized cylinder; Described Pilot operated check valve E1 comprises three inner hydraulic fluid ports: hydraulic fluid port E10, hydraulic fluid port E11 and hydraulic fluid port E12, and hydraulic fluid port E10 is communicated with body cavity PATENT left side via 202 and hydraulic fluid port K1, and hydraulic fluid port E12 is communicated with through hole on valve body 204 and hydraulic fluid port T1, and hydraulic fluid port E11 is communicated with hydraulic fluid port K2;
Described Pilot operated check valve E2 comprises three inner hydraulic fluid ports: hydraulic fluid port E20, hydraulic fluid port E21 and hydraulic fluid port E22, and wherein hydraulic fluid port E21 is for controlling fluid, and hydraulic fluid port E20 and hydraulic fluid port E22 are work fluid; Hydraulic fluid port E20 is communicated with body cavity right side through hole 203, and hydraulic fluid port E22 is communicated with through hole on valve body 208 and hydraulic fluid port T2, and hydraulic fluid port E21 is communicated with hydraulic fluid port K1;
The hydraulic fluid port P mouth that is threaded in outside, is connected with external pressurization cylinder system, and hydraulic fluid port P is communicated with valve hole 206 inner, and hydraulic fluid port P is communicated with by looping pit maintenance radially with hydraulic fluid port P0 simultaneously.
The hydraulic fluid port P0 mouth that is threaded in outside, is connected with external pressurization cylinder system, is connected with the manhole 340 on above-mentioned cylinder barrel 30.
Hydraulic fluid port A is provided at an outer portion with the mouth that is threaded, and is connected with external pressurization cylinder system, is communicated with the manhole 361 on above-mentioned pressurized cylinder; Hydraulic fluid port A is communicated with valve hole 205 inner, is also communicated with hydraulic fluid port M2 simultaneously.
Hydraulic fluid port B is provided at an outer portion with the mouth that is threaded, and is connected with external pressurization cylinder system, is communicated with the manhole 362 on above-mentioned pressurized cylinder; Hydraulic fluid port B is communicated with valve hole 207 inner, is also communicated with hydraulic fluid port N2 simultaneously.
Hydraulic fluid port K1 is provided at an outer portion with the mouth that is threaded, and is connected with external pressurization cylinder system, is communicated with the manhole 352 of above-mentioned pressurized cylinder; Hydraulic fluid port K1 is communicated with PATENT left side via 202 inner, is also communicated with hydraulic fluid port E10, is also communicated with hydraulic fluid port E21.
Hydraulic fluid port K2 is provided at an outer portion with the mouth that is threaded, and is connected with external pressurization cylinder system, is communicated with the manhole 351 of pressurized cylinder; Hydraulic fluid port K2 is communicated with right side through hole 203 inner, is also communicated with hydraulic fluid port E20, is also communicated with hydraulic fluid port E11.
Hydraulic fluid port T outside is provided with the mouth that is threaded, and is connected with the fuel tank of external hydraulic system; In inside, hydraulic fluid port T is communicated with E12 and E22; Hydraulic fluid port T is communicated with hydraulic fluid port T1 by one-way valve, is communicated with hydraulic fluid port T2 by one-way valve; Hydraulic fluid port T1, hydraulic fluid port T2 are equipped with external screw-thread connection mouth, are connected with external pressurization cylinder system, and wherein hydraulic fluid port T1 is communicated with the oil outlet 381 of above-mentioned pressurized cylinder; Hydraulic fluid port T2 is communicated with the oil outlet 382 of above-mentioned pressurized cylinder;
Hydraulic fluid port T communicates with valve hole 204 and valve hole 208.
A kind of pressurization system, comprise above-mentioned pressurized cylinder and above-mentioned integrated valve block, described integrated valve block is connected by pipeline with described pressurized cylinder, its annexation is: the hydraulic fluid port A of integrated valve block is communicated with the manhole 361 of pressurized cylinder, the hydraulic fluid port B of integrated valve block is communicated with the manhole 362 of pressurized cylinder, for supercharging for the first time provides work fluid; The hydraulic fluid port P0 of integrated valve block is communicated with the manhole 340 of pressurized cylinder, for external control devices provides the spool power oil of selector valve; The hydraulic fluid port K1 of integrated valve block is communicated with the manhole 352 of pressurized cylinder, and the hydraulic fluid port K2 of integrated valve block is communicated with the manhole 351 of pressurized cylinder, the direction of action of the spool 220 of control integration valve piece; The hydraulic fluid port T1 of integrated valve block is communicated with the oil outlet 381 of pressurized cylinder, and the hydraulic fluid port T2 of integrated valve block is communicated with the oil outlet 382 of pressurized cylinder, is the secondary booster repairing of pressurized cylinder; On integrated valve block, the hydraulic fluid port M3 of Pilot operated check valve M and the compensation hydraulic fluid port 391 of pressurized cylinder are communicated with, and on integrated valve block, the hydraulic fluid port N3 of Pilot operated check valve N and the compensation hydraulic fluid port 392 of pressurized cylinder are communicated with; The hydraulic fluid port T of integrated valve block is connected with the fuel tank of external hydraulic system; Hydraulic fluid port P has external screw-thread connection mouth, is connected with the high pressure oil of external pressurization system.
Its working procedure of above-mentioned pressurization system is as follows:
As shown in Figure 9, now the spool 220 of integrated valve block in left position.
The high pressure oil that external hydraulic system provides is from the hydraulic fluid port P input of integrated valve block, and now hydraulic fluid port P is divided into two-way, communicates with P0 mouth, also communicates with A mouth.Hydraulic fluid port P0 is communicated with the manhole 340 of pressurized cylinder, the high pressure oil of hydraulic fluid port P0 enters into the commutation of cylinder barrel 30 and controls oily outside filler opening 340, fluid flows to groove 34 by hydraulic fluid port 340, enter into again hydraulic fluid port 271 and hydraulic fluid port 272, now fluid has just rested on hydraulic fluid port 271 and hydraulic fluid port 272, when the groove 12 of wait first stage piston 10 moves to left position or right position, fluid will flow in groove 12 and go.
Because hydraulic fluid port A is communicated with hydraulic fluid port 361, the high pressure oil of hydraulic fluid port A enters the outside hydraulic fluid port 361 of the turnover work fluid of cylinder barrel 30, because hydraulic fluid port 361 is communicated with hydraulic fluid port 291, high pressure oil inwardly enters into again the inside grooved mouth 291 of the turnover work fluid of second piston 20, thereby flow in the left side low-pressure cavity 44 of first stage piston and second piston formation.Due to A
13 ﹥a
14, first stage piston moves right because of the effect of being under pressure, thereby completes supercharging for the first time action, and fluid removes resistance from the space between cylindrical body 23 and disk 24 and flows out, and the rightward space 46 forming from disk 14 and cylindrical body 23 is exported high pressure oil for the first time.
Pressurization for the first time: the relative movement by first stage piston 10 and second piston 20 completes, the pressure size of the pressure oil of supposing the system input is P, the delivery pressure after supercharging is for the first time HP, can obtain following relationship:
P·(A
13-A
14)＝HP·A
14；
The pressure of the high pressure oil of therefore, exporting after supercharging for the first time
The pressure ratio of supercharging for the first time
When first stage piston 10 moves right in process, 45 hydraulic oil in the right side low-pressure cavity being formed by first stage piston and second piston, will flow out by the inside grooved hydraulic fluid port 292 of the turnover work fluid of described second piston 20 right-hand members, hydraulic fluid port 292 is communicated with hydraulic fluid port 362, and then the outside hydraulic fluid port 362 of turnover work fluid by cylinder barrel 30 flow into the external connection screw hydraulic fluid port B of integrated valve block, get back to hydraulic fluid port T by the oil pocket in valve body again, flow back in the fuel tank of external hydraulic system.
The unresisted output in space of high pressure oil between cylindrical body 23 and disk 24 for the first time, enter into the right side low-pressure cavity 47 that second piston 20 and cylinder barrel 30 form, now second piston 20 is moved to the left because being subject to right side high-voltage oil liquid pressure-acting, now complete the action of supercharging for the second time, high pressure oil is exported from hydraulic fluid port 371 in the left side hyperbaric chamber 41 of second piston and cylinder barrel formation.In this simultaneously, the fluid in fuel tank can be entered into one-way valve and entered into via hydraulic fluid port T2 by the hydraulic fluid port T of integrated valve block the filler opening of supercharging for the second time 382 of cylinder barrel 30, is that pressurized cylinder supplements fluid.
Pressurization is to be completed by the relative movement of second piston 20 and cylinder barrel 30 for the second time.Suppose that the high pressure oil of exporting after supercharging is for the second time HHP, can obtain following relationship:
P·(A
13-A
14)+HP·(A
22-A
23-A
25)＝HHP·A
25；
Therefore after supercharging for the second time, the pressure of the high pressure oil of output is:
Secondary pressure ratio is:
The pressure ratio after last twice acting in conjunction of this pressurized cylinder is:
Can see from the formula of deriving, the final pressure ratio R of this pressurized cylinder is the product of twice pressure ratio R1 and R2.From a structural point, the pressure of the fluid of this pressurized cylinder output equals the pressure of the fluid obtaining after two formed objects pressurized cylinders are together in series.Therefore the present invention can utilize very little spatial volume, obtains very large pressure ratio, and in other words, the pressure ratio that pressurized cylinder of the present invention obtains is the secondary power of common pressurized cylinder pressure ratio.Pressurized effect is obvious, and compact structure, without the participation of electrically-controlled valve.
First stage piston 10 moved right after a period of time, when making the commutation of second piston 20 control oily inside filler opening 272 and commutate, the position of groove 12 controls after 282 connections of oily inside oil outlet, the high pressure oil that is arranged in hydraulic fluid port 272 has entered hydraulic fluid port 282, controls oily outside oil outlet 352 and get back to the external connection screw hydraulic fluid port K1 of integrated valve block via the commutation of cylinder barrel 30.High pressure oil in hydraulic fluid port K1 can promote spool 220 and move right, thereby has reached the auto reversive object of spool 220; After spool 220 commutations, change the oil circuit flow direction in integrated valve block, finally made the moving direction of first stage piston 10 also change, realized the automatic reverse of pressurized cylinder inner carrier.
When in the process that the high pressure oil promotion spool 220 in hydraulic fluid port K1 moves right, because hydraulic fluid port K1 is communicated with hydraulic fluid port E21, open Pilot operated check valve E2, make the unnecessary fluid on spool 220 right sides can be discharged to smoothly oil return inlet T.
In the time that spool 220 moves to the position of body cavity 201 right-hand members, the hydraulic fluid port P in integrated valve block is communicated with hydraulic fluid port B, be also communicated with hydraulic fluid port P0 simultaneously, and action below and said process type, moving direction is contrary, full symmetric action.
Pressurization system can be revealed because of the fluid that sealability problem causes in movement process, and the effect of the leakage compensation hydraulic fluid port 391 of cylinder barrel 30 and compensation hydraulic fluid port 392 is just in order to supplement the fluid problem lacking because of leakage.Compensation hydraulic fluid port 391 is communicated with the hydraulic fluid port M3 of integrated valve block, compensation hydraulic fluid port 392 is communicated with the hydraulic fluid port N3 of integrated valve block, when oil hydraulic cylinder produces after leakage, and the inner negative pressure that can produce a certain size, this negative pressure will suck the fluid in fuel tank, supplements to reach the object of revealing.
Preferred scheme is, the height of cylindrical body 13 is greater than two times of distance between hydraulic fluid port 271 and hydraulic fluid port 272.
Preferred scheme is that the height of cylindrical body 22 is greater than 1.5 times of cylindrical body 13 height.
Preferred scheme is, grooved hydraulic fluid port 291 and grooved hydraulic fluid port 292 are positioned at the two ends of cylindrical body 22, and length equals the height of the cylindrical body 22 of 1/3 times.
Claims (1)
1. an integrated valve block, comprise valve body (200), valve body (200) is provided with inner chamber (201), it is characterized in that, described valve body (200) is offered respectively through hole in inner chamber (201) end positions: PATENT left side via (202) and right side through hole (203), described valve body (200) outer wall wall, to five annular through-holes are radially set between inner chamber, is from left to right followed successively by: the first through hole (204), the second through hole (205), third through-hole (206), fourth hole (207), fifth hole (208); Inner chamber (201) inner sleeve cartridge spool (220), described spool (220) arranges four coaxial prismatic cylindrical bodys in the mode keeping at a certain distance away on its axial direction: the first cylindrical body (221), the second cylindrical body (222), three cylindrical body (223) and the 4th cylindrical body (224), and four cylindrical bodys of described spool (200) and described inner chamber (201) coordinate the two-position four way change valve that becomes zero aperture; Described valve body (200) is provided with hydraulic fluid port T, hydraulic fluid port T1, hydraulic fluid port T2, hydraulic fluid port P, hydraulic fluid port P0, hydraulic fluid port A, hydraulic fluid port B, hydraulic fluid port K1, hydraulic fluid port K2, also comprises Pilot operated check valve M, Pilot operated check valve N, Pilot operated check valve E1 and Pilot operated check valve E2;
Described Pilot operated check valve M comprises that two inner hydraulic fluid port M1, M2 are connected outside hydraulic fluid port M3 with one, inner hydraulic fluid port M1 is communicated with inner chamber (201), inner hydraulic fluid port M2 is communicated with the second through hole (205) and outside hydraulic fluid port A on valve body, and outside hydraulic fluid port M3 is communicated with the outside oil circuit of integrated valve block;
Described Pilot operated check valve N comprises that two inner hydraulic fluid port N1, N2 are connected outside hydraulic fluid port N3 with one, inner hydraulic fluid port N1 is communicated with inner chamber (201), inner hydraulic fluid port N2 is communicated with fourth hole on valve body (207) and outside hydraulic fluid port B, and hydraulic fluid port N3 is communicated with the outside oil circuit of integrated valve block;
Described Pilot operated check valve E1 comprises three inner hydraulic fluid port E10, E11, E12, and hydraulic fluid port E10 is communicated with body cavity PATENT left side via (202) and hydraulic fluid port K1, and hydraulic fluid port E12 is communicated with the first through hole (204) and hydraulic fluid port T1 on valve body, and hydraulic fluid port E11 is communicated with hydraulic fluid port K2;
Described Pilot operated check valve E2 comprises three inner hydraulic fluid port E20, E21, E22; Hydraulic fluid port E20 is communicated with body cavity right side through hole (203), and hydraulic fluid port E22 is communicated with fifth hole on valve body (208) and hydraulic fluid port T2, and hydraulic fluid port E21 is communicated with hydraulic fluid port K1;
Hydraulic fluid port P has external screw-thread connection mouth, communicates with the pressure oil of external hydraulic system, and hydraulic fluid port P is communicated with valve body third through-hole (206) inner, keeps being communicated with hydraulic fluid port P0 by looping pit radially simultaneously;
The hydraulic fluid port P0 mouth that is threaded in outside, is connected with external pressurization cylinder system;
Hydraulic fluid port A is provided at an outer portion with the mouth that is threaded, and is connected with external pressurization cylinder system; Hydraulic fluid port A is communicated with valve body the second through hole (205) inner, is also communicated with hydraulic fluid port M2 simultaneously;
Hydraulic fluid port B is provided at an outer portion with the mouth that is threaded, and is connected with external pressurization cylinder system; Hydraulic fluid port B is communicated with valve body fourth hole (207) inner, is also communicated with hydraulic fluid port N2 simultaneously;
Hydraulic fluid port K1 is provided at an outer portion with the mouth that is threaded, and is connected with external pressurization cylinder system; Hydraulic fluid port K1 is communicated with PATENT left side via (202) inner, is also communicated with hydraulic fluid port E10, is also communicated with hydraulic fluid port E21;
Hydraulic fluid port K2 is provided at an outer portion with the mouth that is threaded, and is connected with external pressurization cylinder system; Hydraulic fluid port K2 is communicated with right side through hole (203) inner, is also communicated with hydraulic fluid port E20, is also communicated with hydraulic fluid port E11;
Hydraulic fluid port T outside is provided with the mouth that is threaded, and is connected with the fuel tank of external hydraulic system; In inside, hydraulic fluid port T is communicated with E12 and E22; Hydraulic fluid port T is communicated with hydraulic fluid port T1 by one-way valve, is communicated with hydraulic fluid port T2 by one-way valve; Hydraulic fluid port T1, T2 are equipped with external screw-thread connection mouth, are connected with external pressurization cylinder system;
Hydraulic fluid port T communicates with valve body the first through hole (204) and valve body fifth hole (208).
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| CN201310443710.7A CN103452940B (en) | 2013-09-25 | 2013-09-25 | Integrated valve block |
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|---|---|---|---|
| CN201310443710.7A CN103452940B (en) | 2013-09-25 | 2013-09-25 | Integrated valve block |
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| CN106481603B (en) * | 2015-08-24 | 2018-04-10 | 晋中浩普液压设备有限公司 | Twin-tub super-pressure automatic reciprocating booster |
| CN108591173B (en) * | 2018-05-10 | 2019-08-06 | 安徽江淮汽车集团股份有限公司 | A kind of solenoid valve and double acting two-stage gas cylinder control assembly |
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| JPS5868507A (en) * | 1981-10-20 | 1983-04-23 | Tadano Tekkosho:Kk | Coupling system for plural hydraulic cylinder |
| DE19828199C2 (en) * | 1998-06-25 | 2000-04-20 | Daimler Chrysler Ag | Shut-off valve |
| ITBO20020735A1 (en) * | 2002-11-20 | 2004-05-21 | Marchesini Group Spa | MULTIVIA HYDRAULIC VALVE DEVICE |
| CN101418865B (en) * | 2007-10-22 | 2010-12-22 | 深圳迈瑞生物医疗电子股份有限公司 | Rotary integrated valve |
| CN202510444U (en) * | 2012-03-27 | 2012-10-31 | 裕泰液压技术(上海)有限公司 | Novel integrated control valve block |
| CN102886463B (en) * | 2012-09-24 | 2014-11-05 | 重庆科技学院 | Hydraulic press special for integral compound bulging of automatic driving axle |
| CN103233941B (en) * | 2013-05-07 | 2016-08-17 | 福建海源自动化机械股份有限公司 | Multi-stage booster cylinder and pressurize using method and release using method |
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