CN105570206A - Hydraulic transformer provided with combined port plate - Google Patents
Hydraulic transformer provided with combined port plate Download PDFInfo
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- CN105570206A CN105570206A CN201610102962.7A CN201610102962A CN105570206A CN 105570206 A CN105570206 A CN 105570206A CN 201610102962 A CN201610102962 A CN 201610102962A CN 105570206 A CN105570206 A CN 105570206A
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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
- F15B3/00—Intensifiers or fluid-pressure converters, e.g. pressure exchangers; Conveying pressure from one fluid system to another, without contact between the fluids
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- Fluid Mechanics (AREA)
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- General Engineering & Computer Science (AREA)
- Fluid-Damping Devices (AREA)
- Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
Abstract
The invention discloses a hydraulic transformer provided with a combined port plate and belongs to the technical field of hydraulic parts. The hydraulic transformer is characterized in that an outer plate provided with an inner tooth is arranged outside an inner plate provided with an outer tooth in a sleeving mode; the right end face of the inner plate and the right end face of the outer plate are attached to the left end face of a floating plate; the outer plate inner tooth, the inner plate outer tooth and a floating plate convex tooth are located in the same circular ring groove and divide the circular ring groove into a first arc-shaped groove, a second arc-shaped groove and a third arc-shaped groove; a first oil channel of a rear shell communicates with the first arc-shaped groove through a first oil hole; a second oil channel of the rear shell communicates with the second arc-shaped groove through a second oil hole; a third oil channel of the rear shell communicates with the third arc-shaped groove through a third oil hole; the outer plate is driven by a first swing motor to rotate through a spline; the inner plate is driven by a second motor to rotate through a spline; the floating plate is connected with the rear shell through a pin shaft; the swing angle of the inner plate and the swing angle of the outer plate are both within the range of 0 degree to 140+/-10 degrees. The hydraulic transformer has the advantages that the hydraulic transformer has large transformer ratio and is capable of effectively reducing vibration and noise, and servo control can be achieved easily.
Description
Technical field
The invention belongs to hydraulic parts technical field, be specifically related to a kind of hydraulic transformer with combined type thrust plate.
Background technique
Constant pressure network Secondary Regulation Technology is the very important energy-saving scheme in current hydraulic transmission field.But, due to core parts--the technology of hydraulic transformer is immature, and constant pressure network technology is difficult to be promoted always.Domestic and international multinomial patent and paper have carried out theoretical and experimental research to hydraulic transformer, face multinomial technical barrier, wherein two key technology difficult problems are: (1) hydraulic transformer thrust plate has the identical kidney slot of three shapes, in cylinder body rotary course, plunger cavity internal pressure constantly changes, when plunger case forwards another kidney slot to from a kidney slot, fluid in plunger cavity is temporarily cut off by the valve face between two kidney slots, cut-off during this period of time in, plunger case cavity volume is large or reduce by change, generation is expanded or compression by the fluid in cavity, very high pressure peak or serious cavitation can be caused like this to produce, cause the increase of noise.Can not solve noise problem very well by opening Silencing groove between kidney slot, InnasBV company introduces " shuttle " technological scheme, in reduction pressure peak and noise, obtain certain effect; (2) three fixing kidney slots on thrust plate also cause transformation ratio scope less, and researchers have employed multiple Optimal improvements measure, but transformation ratio scope still can not practical requirement.
Summary of the invention
The object of the invention is to provide a kind of hydraulic transformer with combined type thrust plate, effectively can overcome problems of the prior art.The object of the present invention is achieved like this, as shown in Fig. 1 ~ Fig. 8, it comprises front case 1, rear case 11, front cover 21, rear end cover 14, running shaft 3, plunger 5, plunger case 6, front cover 21 is arranged on the end of front case 1 by spring flange 20, rear end cover 14 is arranged on the end face of rear case 11 by second group of bolt 12, front case 1 and rear case 11 are linked together by first group of bolt 9, running shaft 3 is arranged in the center cavity of front case 1 leading portion by clutch shaft bearing 2 and the second bearing 4, plunger case 6 is connected with the ball-and-socket on running shaft 3 ear end face by the bulb of n plunger 5, plunger case 6 and n plunger 5 define n plunger cavity 7, n is positive integer, running shaft 3 and plunger case 6, both axis intersect with sharp angle α in same plane, the present invention is characterized in that:
The outer disk 17 being shaped with outer disk internal tooth 17.1 is sleeved on the outside of the inner disc 18 being shaped with inner disc external tooth 18.1, fit in the right side of inner disc 18 and outer disk 17 and the left side of floating disc 16, the left side of inner disc 18 and outer disk 17 and the Topland of double wedge 16.1 are fitted with the concave spherical surface of plunger case 6 right-hand member respectively, floating disc 16 is arranged in the center cavity of rear case 11 left end, be connected with rear case 11 by locating stud 10, first rotary actuator rotor 8 is connected with outer disk 17 by the first spline J1, the the first rotary actuator rotor 8 being shaped with the first external tooth 8.1 and the second external tooth 8.2 is arranged on front case 1 and is shaped with between the end face of rear case 11 of the first internal tooth 11.1 and the second internal tooth 11.2, second rotary actuator rotor 13 is connected with inner disc 18 by the second spline J2 through rear case 11 and floating disc 16, the the second rotary actuator rotor 13 being shaped with the first external tooth 13.1 and the second external tooth 13.2 is arranged in the center cavity of rear case 11, rear end cover 14 is connected with the end face of rear case 11 by the second bolt group 12,
As shown in Figure 2, in said structure, outer disk internal tooth 17.1, inner disc external tooth 18.1 and double wedge 16.1 coexist in annular groove 32, annular groove 32 are divided into first, second, third curve bath 22,23,24, as shown in Figure 4, the first oil duct 25 in rear case 11 is communicated with plunger cavity 7 with the first curve bath 22 by the first oilhole 28 on floating disc 16, second oil duct 26 of rear case 11 is communicated with plunger cavity 7 with the second curve bath 23 by the second oilhole 29 on floating disc 16, 3rd oil duct 15 of rear case 11 is communicated with plunger cavity 7 with the 3rd curve bath 24 by the 3rd oilhole 30 on floating disc 16, the first rotary actuator rotor first external tooth 8.1, first rotary actuator rotor second external tooth 8.2, rear case first internal tooth 11.1 and rear case second internal tooth 11.2 are positioned at the first annular chamber Q1, and the first annular chamber Q1 is divided into the first rotary actuator first, second, 3rd, 4th active chamber A1, B1, C1, D1, respectively with the first rotary actuator first, second, 3rd, 4th hydraulic fluid port a1, b1, c1, d1 is communicated with, the second rotary actuator rotor first external tooth 13.1, second rotary actuator rotor second external tooth 13.2, rear case the 3rd internal tooth 11.3 and rear case the 4th internal tooth 11.4 are positioned at the second annular chamber Q2, and the second annular chamber Q2 is divided into the second rotary actuator first, second, 3rd, 4th active chamber A2, B2, C2, D2, respectively with the second rotary actuator first, second, 3rd, 4th hydraulic fluid port a2, b2, c2, d2 is communicated with,
First, second, third oilhole 28,29,30 of described floating disc 16 and double wedge 16.1 are positioned at toroidal surface 31, double wedge 16.1 and low pressure oilhole 30 lay respectively at extreme higher position and the extreme lower position of toroidal surface 31, first oilhole 28 is near the side of double wedge 16.1, and high pressure oilhole 29 is near the opposite side of double wedge 16.1;
The Topland of described outer disk internal tooth 17.1 and the intrados of double wedge 16.1 are 3 ~ 8um with the matching gap of the periphery of inner disc 18 respectively, the Topland of inner disc external tooth 18.1 and the outer arced surface of double wedge 16.1 are 3 ~ 8um with the matching gap of the inner headed face of outer disk 17 respectively, toroidal surface 31, the toroidal surface at the oilhole place of the ear end face of annular groove 32 and plunger case 6 is just right, outer disk internal tooth 17.1, inner disc external tooth 18.1, double wedge 16.1 is 1 ~ 2 times of the oilhole diameter of plunger case 6 ear end face at the width at 1/2 tooth depth place, double wedge 16.1 and the straight line at central point place of low pressure oilhole 30 and the axis co-planar of the axis of running shaft 3 and plunger case 6, the angle of the extreme higher position P1 of outer disk internal tooth 17.1 in annular groove 32 and extreme lower position P2 is θ 1, the angle of the extreme higher position P3 of inner disc external tooth 18.1 in annular groove 32 and extreme lower position P4 is θ 2, so the pendulum angle scope of outer disk 17 and inner disc 18 is respectively 0 ~ θ 1 and 0 ~ θ 2, the angle value of θ 1 and θ 2 is 140 ± 20 °,
Described floating disc also can rotate 180 ° of installations, rear case 11 also corresponding rotation 180 ° installation;
Advantage of the present invention and good effect are:
(1) by adopting combined type thrust plate scheme, the size of the high pressure curve bath of the thrust plate of hydraulic transformer, load curve bath and low pressure curve bath can regulate in a big way, and high pressure curve bath and load curve bath can independent variation, the transformation ratio scope of hydraulic transformer significantly improves.
(2) in high pressure curve bath, load curve bath and low pressure curve bath, the interval of any two curve baths is only the width of an external tooth or internal tooth or double wedge, gap length between adjacent curve bath significantly reduces, occur that pressure increases sharply when avoiding plunger cavity to move between two curve baths, significantly reduce noise and cavitation erosion.
(3) outer disk and inner disc are driven by independent rotary actuator respectively, are easy to realize servocontrol, realize the high response characteristic of hydraulic transformer.
Accompanying drawing explanation
Fig. 1 is the structural profile schematic diagram of hydraulic transformer.
Fig. 2 is A-A sectional view of Fig. 1.
Fig. 3 is B-B sectional view of Fig. 1.
Fig. 4 (b) is the sectional view of rear case.
Fig. 4 (a) is the left view of Fig. 4 (b).
Fig. 4 (c) is the right elevation of Fig. 4 (b).
Fig. 4 (d) is C-C sectional view of Fig. 4 (c).
Fig. 5 (b) is the front view of outer disk.
The left view of Fig. 5 (b) that Fig. 5 (a) is.
Fig. 6 (b) is the front view of inner disc.
The left view of Fig. 6 (b) that Fig. 6 (a) is.
Fig. 7 (b) is the front view of floating disc.
The left view of Fig. 7 (b) that Fig. 7 (a) is.
Fig. 8 is inner disc and outer disk hunting range schematic diagram.
In figure: 1-front case, 2-clutch shaft bearing, 3-running shaft, 4-second bearing, 5-plunger, 6-plunger case, 7-plunger cavity, 8-first rotary actuator rotor, 8.1-first rotary actuator rotor first external tooth, 8.2-first rotary actuator rotor second external tooth, 9-first group of bolt, 10-locating stud, 11-rear case, 11.1-rear case first internal tooth, 11.2-rear case second internal tooth, 11.3-rear case the 3rd internal tooth, 11.4-rear case the 4th internal tooth, 12-second group of bolt, 13-second rotary actuator rotor, 13.1-second rotary actuator rotor first external tooth, 13.2-second rotary actuator rotor second external tooth, 14-rear end cover, 15-the 3rd oil duct, 16-floating disc, 16.1-double wedge, 17-outer disk, 17.1-outer disk internal tooth, 18-inner disc, 18.1-inner disc external tooth, 19-spacer, 20-check ring, 21-front cover, 22-first curve bath, 23-second curve bath, 24-the 3rd curve bath, 25-first oil duct, 26-second oil duct, 27-positioning pin hole, 28-first oilhole, 29-second oilhole, 30-the 3rd oilhole, 31-toroidal surface, 32-annular groove, first active chamber of A1-first rotary actuator, second active chamber of B1-first rotary actuator, 3rd active chamber of C1-first rotary actuator, 4th active chamber of D1-first rotary actuator, first active chamber of A2-second rotary actuator, second active chamber of B2-second rotary actuator, 3rd active chamber of C2-second rotary actuator, 4th active chamber of D2-second rotary actuator, first hydraulic fluid port of a1-first rotary actuator, second hydraulic fluid port of b1-first rotary actuator, 3rd hydraulic fluid port of c1-first rotary actuator, 4th hydraulic fluid port of d1-first rotary actuator, first hydraulic fluid port of a2-second rotary actuator, second hydraulic fluid port of b2-second rotary actuator, 3rd hydraulic fluid port of c2-second rotary actuator, 4th hydraulic fluid port of d2-second rotary actuator, the extreme higher position of P1-outer disk internal tooth, the extreme lower position of P2-outer disk internal tooth, the extreme higher position of P3-inner disc external tooth, the extreme lower position of P4-inner disc external tooth, J1-first spline, J2-second spline, Q1-first annular chamber, Q2-second annular chamber, the maximum pendulum angle of θ 1-outer disk 17, the maximum pendulum angle of θ 2-inner disc 18.
Embodiment
Below in conjunction with drawings and Examples, the present invention is described in further detail.
As shown in Figure 1, this hydraulic transformer is a kind of inclined shaft type hydraulic transformer, and front cover 21, front case 1, rear case 11 and rear end cover 14 constitute the closed cavity volume of inclined shaft type hydraulic transformer; Front cover 21 does not open hole, and running shaft 3, completely in the inside of closed cavity volume, improves the sealing of enclosed cavity; Running shaft 3 is arranged in the center cavity of front case 1 by clutch shaft bearing 2 and the second bearing 4, angle α=20 ° of the axis of running shaft 3 and the axis of plunger case 6, in the process that running shaft 3 and plunger case 6 rotate simultaneously, there is fore and aft motion in plunger 5, plunger cavity will realize oil suction and oil extraction in plunger cavity 7;
As depicted in figs. 1 and 2, be shaped with the first rotary actuator rotor 8 of two external tooths, front case 1 and rear case 11 constitute a double-leaf rotary actuator jointly, double-leaf motor is to the symmetrically formula distribution of the active force of housing, outside oil sources high pressure fuel source and low pressure oil sources are by first of the first rotary actuator, second, third and fourth hydraulic fluid port a1, b1, c1, d1 gives first of the first rotary actuator, second, third and fourth active chamber A1, B1, C1, D1 fuel feeding and oil extraction, first rotary actuator rotor 8 drives outer disk 17 to realize swinging by the first spline J1, the pendulum angle of the first rotary actuator rotor 8 equals the pendulum angle θ 1 of outer disk 17, θ 1=140 °,
As depicted in figs. 1 and 2, be shaped with the second rotary actuator rotor 13 of two external tooths, rear case 11 and rear end cover 14 constitute a double-leaf rotary actuator jointly, external high pressure oil sources and low pressure oil sources are by first of the second rotary actuator, second, third and fourth hydraulic fluid port a2, b2, c2, d2 gives first of the second rotary actuator, second, third and fourth active chamber A2, B2, C2, D2 fuel feeding and oil extraction, second rotary actuator rotor 13 drives inner disc 18 to realize swinging by the second spline J2, the pendulum angle of the second rotary actuator rotor 13 equals the pendulum angle θ 2 of inner disc 18, θ 2=140 °,
As shown in Fig. 1,2,5,6,7, inner disc 18, outer disk 17 and floating disc 16 constitute thrust plate jointly, replace existing hydraulic transformer monomer-type thrust plate;
Outer disk 17 is sleeved on the outside of inner disc 18, fits in the right side of inner disc 18 and outer disk 17 and the left side of floating disc 16; The Topland of inner disc external tooth 18.1 and the outer arced surface of double wedge 16.1 are 4um with the matching gap of the inner headed face of outer disk 17 respectively, the Topland of outer disk internal tooth 17.1 and the intrados of double wedge 18.1 are 4um with the matching gap of the periphery of inner disc 18 respectively, such micro-gap can realize lubrication on the one hand, amount of leakage is also very little on the other hand, and annular groove 32 is just split in order to first, second, third curve bath 22,23,24 by such three teeth;
Floating disc 16 is connected with rear case 11 by locating stud 10, floating disc 16 cannot rotate relative to rear case 11 on the one hand, in working procedure, the right side of floating disc 16 pushes outer disk 17 and inner disc 18 under pressure oil effect on the other hand, the concave spherical surface of the convex spherical of the left end of combined type thrust plate and plunger case 6 rear end is fitted, so can form hydrostatic support means of press seals district between faying surface, can realize lubrication on the one hand, amount of leakage is also very little on the other hand;
Dead zone location in the extreme higher position of toroidal surface 31 residing for double wedge 16.1 and plunger case 6 rotary course, the pressure significantly reduced in plunger cavity 7 increases sharply;
First hydraulic fluid port 28 and the second hydraulic fluid port 29 lay respectively at the both sides of double wedge 16.1, and the 3rd hydraulic fluid port 30 is positioned at the extreme lower position of toroidal surface 31, and this location arrangements can make the pendulum angle θ 1 of inner disc 18 and outer disk 17, θ 2 reaches maximum;
Outer disk internal tooth 17.1, inner disc external tooth 18.1, double wedge 16.1 are 1.5 times of the oilhole diameter of plunger case 6 ear end face at the width at 1/2 tooth depth place, not only avoid in working procedure and realize being communicated with by the oilhole of plunger case 6 ear end face between adjacent curve bath, and can effectively prevent plunger cavity 7 internal pressure from increasing sharply;
The toroidal surface at the oilhole place of the ear end face of toroidal surface 31, annular groove 32 and plunger case 6 is just right, and the internal diameter of three and external diameter are all identical, and whole oil circuit can be made to avoid occurring larger part throttle loss;
As shown in figures 1 and 3, open the first oil duct 25, second oil duct 26 in rear case 11 to be connected with external high pressure oil sources, load oil sources and low pressure oil sources respectively with the 3rd oil duct 15, so high pressure fuel source will be communicated with one or more plunger cavity 7 through the first oil duct 25, first oilhole 28, first curve bath 22, load oil sources will be communicated with one or more plunger cavity 7 through the second oil duct 26, second oilhole 29, second curve bath 23, and low pressure oil sources will be communicated with one or more plunger cavity 7 through the 3rd oil duct 15, the 3rd oilhole 30, the 3rd curve bath 24;
Inner disc 18 rotates relative to floating disc 16, the area of the first, the 3rd curve bath 22,24 is changed, outer disk 17 rotates relative to floating disc 16, the area of second, third curve bath 23,24 is changed, so the number of the plunger cavity 7 of three curve bath connections also can change, and causes the pressure ratio in the first curve bath 22 and the second curve bath 23 to change;
Adopt the first rotary actuator rotor 8 and the second rotary actuator rotor 13 to drive outer disk 17 and inner disc 18 to rotate respectively, the change speed of response of hydraulic transformer delivery pressure and output flow can be significantly improved.
As shown in Figure 1, floating disc 16 can rotate 180 ° of installations, and rear case 11 also corresponding rotation 180 ° installation, can realize the function of hydraulic transformer equally.
Claims (2)
1. one kind has the hydraulic transformer of combined type thrust plate, it comprises front case (1), rear case (11), front cover (21), rear end cover (14), running shaft (3), plunger (5), plunger case (6), front cover (21) is arranged on the end of front case (1) by spring flange (20), rear end cover (14) is arranged on the end face of rear case (11) by second group of bolt (12), front case (1) and rear case (11) are linked together by first group of bolt (9), running shaft (3) is arranged in the center cavity of front case (1) leading portion by clutch shaft bearing (2) and the second bearing (4), plunger case (6) is connected with the ball-and-socket on running shaft (3) ear end face by the bulb of n plunger (5), plunger case (6) and n plunger (5) define n plunger cavity (7), n is positive integer, running shaft (3) and both axis of plunger case (6) intersect with sharp angle α in same plane, the present invention is characterized in that:
The outer disk (17) being shaped with outer disk internal tooth (17.1) is sleeved on the outside of the inner disc (18) being shaped with inner disc external tooth (18.1), fit in the right side of inner disc (18) and outer disk (17) and the left side of floating disc (16), the left side of inner disc (18) and outer disk (17) and the Topland of double wedge (16.1) are fitted with the concave spherical surface of plunger case (6) right-hand member respectively, floating disc (16) is arranged in the center cavity of rear case (11) left end, be connected with rear case (11) by locating stud (10), first rotary actuator rotor (8) is connected with outer disk (17) by the first spline J1, the the first rotary actuator rotor (8) being shaped with the first external tooth (8.1) and the second external tooth (8.2) is arranged between front case (1) and the end face of rear case (11) being shaped with the first internal tooth (11.1) and the second internal tooth (11.2), second rotary actuator rotor (13) is connected with inner disc (18) by the second spline J2 through rear case (11) and floating disc (16), the the second rotary actuator rotor (13) being shaped with the first external tooth (13.1) and the second external tooth (13.2) is arranged in the center cavity of rear case (11), rear end cover (14) is connected with the end face of rear case (11) by the second bolt group (12),
In said structure, outer disk internal tooth (17.1), inner disc external tooth (18.1) and double wedge (16.1) coexist in annular groove (32), and annular groove (32) is divided into first, second, 3rd curve bath (22, 23, 24) the first oil duct (25), in rear case (11) is by the first oilhole (28), first curve bath (22) is communicated with plunger cavity (7), and the second oil duct (26) in rear case (11) is by the second oilhole (29), second curve bath (23) is communicated with plunger cavity (7), and the 3rd oil duct (15) in rear case (11) is by the 3rd oilhole (30), 3rd curve bath (24) is communicated with plunger cavity (7), the first rotary actuator rotor first external tooth (8.1), first rotary actuator rotor second external tooth (8.2), rear case first internal tooth (11.1) and rear case second internal tooth (11.2) are positioned at the first annular chamber (Q1), and the first annular chamber (Q1) is divided into the first rotary actuator first, second, 3rd, 4th active chamber (A1, B1, C1, D1), respectively with the first rotary actuator first, second, 3rd, 4th hydraulic fluid port (a1, b1, c1, d1) be communicated with, the second rotary actuator rotor first external tooth (13.1), second rotary actuator rotor second external tooth (13.2), rear case the 3rd internal tooth (11.3) and rear case the 4th internal tooth (11.4) are positioned at the second annular chamber (Q2), and the second annular chamber (Q2) is divided into the second rotary actuator first, second, 3rd, 4th active chamber (A2, B2, C2, D2), respectively with the second rotary actuator first, second, 3rd, 4th hydraulic fluid port (a2, b2, c2, d2) be communicated with,
First, second, third oilhole (28,29,30) and double wedge (16.1) are positioned at toroidal surface (31), double wedge (16.1) and low pressure oilhole (30) lay respectively at extreme higher position and the extreme lower position of toroidal surface (31), first oilhole (28) is near the side of double wedge (16.1), and high pressure oilhole (29) is near the opposite side of double wedge (16.1).
2. inner disc as claimed in claim 1, outer disk and floating disc, it is characterized in that: the Topland of outer disk internal tooth (17.1) and the intrados of double wedge (16.1) are 3 ~ 8um with the matching gap of the periphery of inner disc (18) respectively, the Topland of inner disc external tooth (18.1) and the outer arced surface of double wedge (16.1) are 3 ~ 8um with the matching gap of the inner headed face of outer disk (17) respectively, toroidal surface (31), the toroidal surface at the oilhole place of the ear end face of annular groove (32) and plunger case (6) is just right, outer disk internal tooth (17.1), inner disc external tooth (18.1), double wedge (16.1) is 1 ~ 2 times of the oilhole diameter of plunger case (6) ear end face at the width at 1/2 tooth depth place, double wedge (16.1) and the straight line at central point place of low pressure oilhole (30) and the axis co-planar of the axis of running shaft (3) and plunger case (6), the extreme higher position (P1) of outer disk internal tooth (17.1) in annular groove (32) is θ 1 with the angle of extreme lower position (P2), the extreme higher position (P3) of inner disc external tooth (18.1) in annular groove (32) is θ 2 with the angle of extreme lower position (P4), so the pendulum angle scope of outer disk (17) and inner disc (18) is respectively 0 ~ θ 1 and 0 ~ θ 2, the angle value of θ 1 and θ 2 is 140 ± 20 °.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610102962.7A CN105570206B (en) | 2016-02-24 | 2016-02-24 | A kind of hydraulic transformer with combined type valve plate |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610102962.7A CN105570206B (en) | 2016-02-24 | 2016-02-24 | A kind of hydraulic transformer with combined type valve plate |
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| Publication Number | Publication Date |
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| CN105570206A true CN105570206A (en) | 2016-05-11 |
| CN105570206B CN105570206B (en) | 2017-05-31 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201610102962.7A Active CN105570206B (en) | 2016-02-24 | 2016-02-24 | A kind of hydraulic transformer with combined type valve plate |
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Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4174925A (en) * | 1977-06-24 | 1979-11-20 | Cedomir M. Sliepcevich | Apparatus for exchanging energy between high and low pressure systems |
| US6116138A (en) * | 1996-02-23 | 2000-09-12 | Innas Free Piston B.V. | Pressure transformer |
| CN2643049Y (en) * | 2003-06-02 | 2004-09-22 | 浙江大学 | Hydraulic pressure transformer |
| CN101435417A (en) * | 2008-12-12 | 2009-05-20 | 北京理工大学 | Hydraulic transformer for increasing voltage ratio regulation scope |
| CN101614226A (en) * | 2009-07-14 | 2009-12-30 | 刘顺安 | Internal opening hydraulic transformer and voltage-transforming method |
| CN101634316A (en) * | 2009-06-09 | 2010-01-27 | 东华大学 | Hydraulic transformer with safety device |
| WO2012171519A2 (en) * | 2011-06-14 | 2012-12-20 | Schaeffler Technologies AG & Co. KG | Hydraulic transformer |
-
2016
- 2016-02-24 CN CN201610102962.7A patent/CN105570206B/en active Active
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4174925A (en) * | 1977-06-24 | 1979-11-20 | Cedomir M. Sliepcevich | Apparatus for exchanging energy between high and low pressure systems |
| US6116138A (en) * | 1996-02-23 | 2000-09-12 | Innas Free Piston B.V. | Pressure transformer |
| CN2643049Y (en) * | 2003-06-02 | 2004-09-22 | 浙江大学 | Hydraulic pressure transformer |
| CN101435417A (en) * | 2008-12-12 | 2009-05-20 | 北京理工大学 | Hydraulic transformer for increasing voltage ratio regulation scope |
| CN101634316A (en) * | 2009-06-09 | 2010-01-27 | 东华大学 | Hydraulic transformer with safety device |
| CN101614226A (en) * | 2009-07-14 | 2009-12-30 | 刘顺安 | Internal opening hydraulic transformer and voltage-transforming method |
| WO2012171519A2 (en) * | 2011-06-14 | 2012-12-20 | Schaeffler Technologies AG & Co. KG | Hydraulic transformer |
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| Publication number | Publication date |
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| CN105570206B (en) | 2017-05-31 |
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