CN1124418C - Hydraulic servo device - Google Patents
Hydraulic servo device Download PDFInfo
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- CN1124418C CN1124418C CN98103096.3A CN98103096A CN1124418C CN 1124418 C CN1124418 C CN 1124418C CN 98103096 A CN98103096 A CN 98103096A CN 1124418 C CN1124418 C CN 1124418C
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- 238000004891 communication Methods 0.000 claims abstract description 6
- 239000000446 fuel Substances 0.000 claims description 31
- 238000000605 extraction Methods 0.000 claims description 25
- 230000008878 coupling Effects 0.000 claims description 18
- 238000010168 coupling process Methods 0.000 claims description 18
- 238000005859 coupling reaction Methods 0.000 claims description 18
- 230000002093 peripheral effect Effects 0.000 claims description 16
- 239000002245 particle Substances 0.000 claims description 11
- 230000008859 change Effects 0.000 claims description 4
- 239000012530 fluid Substances 0.000 claims 2
- 238000006073 displacement reaction Methods 0.000 description 7
- 230000004043 responsiveness Effects 0.000 description 6
- 230000006835 compression Effects 0.000 description 5
- 238000007906 compression Methods 0.000 description 5
- 239000000284 extract Substances 0.000 description 3
- 230000014509 gene expression Effects 0.000 description 3
- 230000004044 response Effects 0.000 description 3
- 230000006872 improvement Effects 0.000 description 2
- 238000012423 maintenance Methods 0.000 description 2
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 2
- 230000001133 acceleration Effects 0.000 description 1
- 230000003321 amplification Effects 0.000 description 1
- 230000008901 benefit Effects 0.000 description 1
- 238000004140 cleaning Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000009931 harmful effect Effects 0.000 description 1
- 238000007689 inspection Methods 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
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- 238000003199 nucleic acid amplification method Methods 0.000 description 1
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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
- F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
- F15B21/04—Special measures taken in connection with the properties of the fluid
- F15B21/044—Removal or measurement of undissolved gas, e.g. de-aeration, venting or bleeding
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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
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/08—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor
- F15B11/12—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor providing distinct intermediate positions; with step-by-step action
- F15B11/121—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor providing distinct intermediate positions; with step-by-step action providing distinct intermediate positions
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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
- F15B9/00—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member
- F15B9/02—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member with servomotors of the reciprocatable or oscillatable type
- F15B9/08—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member with servomotors of the reciprocatable or oscillatable type controlled by valves affecting the fluid feed or the fluid outlet of the servomotor
- F15B9/10—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member with servomotors of the reciprocatable or oscillatable type controlled by valves affecting the fluid feed or the fluid outlet of the servomotor in which the controlling element and the servomotor each controls a separate member, these members influencing different fluid passages or the same passage
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- Physics & Mathematics (AREA)
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- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Actuator (AREA)
Abstract
A cylinder houses an angularly movable pilot shaft and a piston axially movably mounted on the pilot shaft. When the pilot shaft is angularly moved, a communication passage defined in an outer circumferential surface of the pilot shaft is brought into communication with an oil supply passage or an oil drain passage for axially moving the piston. The pilot shaft has a pair of communication passages defined in the outer circumferential surface thereof, and the piston has a pair of oil passages defined therein.
Description
Technical field
The present invention relates to a little angle of torsion shift transformation is become the hydraulic servo device of a big load straight-line displacement, particularly be used for handling one as the bucket pipe of the speed-control mechanism of a speed change hydrodynamic coupling hydraulic servo device.
Background technique
Figure 11 illustrates an actuator to the water supply installation of a high power capacity boiler water supply.As shown in figure 11, the rotation of input shaft 121 is through a gearwheel 122 and a small gear 124 acceleration and pass to a driving shaft 123, and this rotation is passed to a driven shaft 125 through a hydrodynamic coupling C then.An output shaft 132 is quickened and passed to this rotation from driven shaft 125 through a gearwheel 131 and a small gear 133 then.Hydrodynamic coupling C comprises an impeller 126 and an impeller housing 128 that is contained on the driving shaft 123 and is contained in a rotor on the driven shaft 125.When in the working room that working oil is introduced on the impeller housing 128, impeller 126 rotates by the viscosity engagement of working oil with rotor 127, thereby passes to driven shaft 125 rotating from driving shaft 123.
Have one to regulate the bucket pipe 130 of working oil flow rate in this working room.It is this hydrodynamic coupling of may command C institute torque transmitted that the shift-in of this bucket pipe 130 in the working room shifts out.This hydrodynamic coupling C simple in structure can continuously change the rotating speed of load one side shaft (output shaft) between minimum and top speed.
The bucket pipe must bear the working oil oil pressure, so its location is accurately essential.A kind of actuator of bucket pipe for example comprises an amplification and transmit the displacement that an electric actuator is generated under a little power, for example visible Japanese patent laid-open publication gazette No.7-208499.The disclosed hydraulic servo device of this patent comprises the piston on the axis of guide that is contained in slidably in the oil hydraulic cylinder, on the axis of guide surface He on the piston internal surface oil duct is arranged.The rotational transform of the axis of guide is exported from hydraulic servo device after becoming the displacement of piston.The position of bucket pipe is positioned at the signal that the displacement transducer on the precalculated position sends by one and carries out feedback control.
For whole machine balancing, the volume of above-mentioned hydraulic servo device must reduce, and in order to satisfy this condition, the diameter of the axis of guide must reduce.But along with reducing of axis of guide diameter, the width that is used as the groove of oil duct on the axis of guide surface also reduces.When the rotating speed of the axis of guide improves, the lip-deep oil duct of the axis of guide shift out with piston in the oil duct positions aligning, cause Control Failure.Therefore, the control response of this hydraulic servo device is restricted.
Summary of the invention
Therefore an object of the present invention is to provide a kind of hydraulic servo device, even very little two oil ducts that also can keep of the diameter of its axis of guide are aligned with each other, even and the less control response of volume also enough good.
According to one aspect of the invention, a kind of hydraulic servo device is provided, comprising: an oil hydraulic cylinder; One extends in the axis of guide of this oil hydraulic cylinder on axially rotationally, and a pair of connection oil duct is arranged on the outer peripheral surface of this axis of guide; One be contained in slidably on this axis of guide and in this oil hydraulic cylinder axially movable piston, a pair of oil duct is arranged in this piston; And an actuator, this actuator makes this axis of guide around its rotational, is communicated with at least one oil duct thereby make at least one be communicated with oil duct, thereby high pressure oil is acted on the piston and makes piston axially mobile in oil hydraulic cylinder.These diameter and width that are communicated with oil duct and oil duct are less, can interconnect in the big rotation angle of the axis of guide, thereby the control response degree of this hydraulic servo device improve.Wherein, being communicated with oil duct is arranged to the relative position of oil duct: the angle range that causes an oil duct to be communicated with the axis of guide of oil duct connection with differs from one another with the angle range that causes another oil duct to be communicated with the axis of guide of oil duct connection with another.
Each is communicated with the curved shape of oil duct.
Oil duct comprises that one supplies the fuel feeding oil duct and an oil extraction oil duct that is connected with an oil exit pipe of working oil under pressure.
According to another aspect of the present invention, a kind of hydraulic servo device is provided, comprising: an oil hydraulic cylinder; One extends in the axis of guide of this oil hydraulic cylinder on axially rotationally, has one to be communicated with oil duct on the outer peripheral surface of this axis of guide; One be contained in slidably on this axis of guide and in this oil hydraulic cylinder axially movable piston, an oil duct is arranged in this piston; One actuator, this actuator makes this axis of guide around its rotational, thereby this connection oil duct is communicated with this oil duct, thereby high pressure oil is acted on the piston and piston is axially moved in oil hydraulic cylinder, the inner space of this oil hydraulic cylinder is separated into first space and second space by this piston, first space is communicated with a high pressure oilhole, and whether second space is communicated with by this connection oil duct selection with this oil duct; A thereby and gas outlet that is connected with the top of this oil hydraulic cylinder with second spatial communication.The compressible air that is trapped in second space can be discharged through this gas outlet, thereby improves the responsiveness of this hydraulic servo device.
This gas outlet has an air outlet hole to be discharged in the atmosphere for air.
This gas outlet has a safety check to be discharged in the atmosphere for air.
According to another aspect of the present invention, a kind of hydraulic servo device is provided, comprising: an oil hydraulic cylinder; One extends in the axis of guide of this oil hydraulic cylinder on axially rotationally, has one to be communicated with oil duct on the outer peripheral surface of this axis of guide; One be contained in slidably on this axis of guide and in this oil hydraulic cylinder axially movable piston, an oil duct is arranged in this piston; One actuator, this actuator makes this axis of guide around its rotational, thereby this connection oil duct is communicated with this oil duct, thereby high pressure oil is acted on the piston and piston is axially moved in oil hydraulic cylinder, the inner space of this oil hydraulic cylinder is separated into first space and second space by this piston, first space is communicated with a high pressure oilhole, whether second space is communicated with by this connection oil duct selection with this oil duct, this oil hydraulic cylinder has the dimple of collection particle wherein, and this dimple lays respectively in first space and/or second space of oil hydraulic cylinder inner peripheral surface bottom.In this dimple, so they can't be clipped between piston and the oil hydraulic cylinder by the particle collection that relative movement generated between piston and the oil hydraulic cylinder, thereby make this hydraulic servo device smooth working.
There is a tap hole to discharge the particle that is collected in this dimple in the cylindrical wall of this oil hydraulic cylinder.
According to another aspect of the present invention, a kind of hydraulic servo device is provided, comprising: an oil hydraulic cylinder; One extends in the axis of guide of this oil hydraulic cylinder on axially rotationally, has one to be communicated with oil duct on the outer peripheral surface of this axis of guide; One be contained in slidably on this axis of guide and in this oil hydraulic cylinder axially movable piston, an oil duct is arranged in this piston; One actuator, this actuator makes this axis of guide around its rotational, thereby this connection oil duct is communicated with this oil duct, thereby high pressure oil is acted on the piston and piston is axially moved in oil hydraulic cylinder, the inner space of this oil hydraulic cylinder is separated into first space and second space by this piston, first space is communicated with a high pressure oilhole, and whether second space is communicated with by this connection oil duct selection with this oil duct; An and oil storage tank that covers an end wall that defines first space of this oil hydraulic cylinder.
According to another aspect of the present invention, a kind of hydraulic servo device is provided, comprising: an oil hydraulic cylinder; One extends in the axis of guide of this oil hydraulic cylinder on axially rotationally, has one to be communicated with oil duct on the outer peripheral surface of this axis of guide; One be contained in slidably on this axis of guide and in this oil hydraulic cylinder axially movable piston, an oil duct is arranged in this piston; One actuator, this actuator make this axis of guide around its rotational, thereby this connections oil duct is communicated with this oil duct, thereby high pressure oil is acted on the piston and make piston axially mobile in oil hydraulic cylinder; There is connection set to be connected on one end face of this piston, so that from oil hydraulic cylinder, pull out piston with a piston stripping attachment.Piston can use the piston stripping attachment that is connected with connection set on the piston to take out from oil hydraulic cylinder at an easy rate.Therefore, be easy to check, keep in repair or change piston, oil hydraulic cylinder and be contained in bucket pipe on the piston.
According to another aspect of the present invention, a kind of hydrodynamic coupling is provided, comprising: can be contained in an impeller and an impeller housing on the driving shaft, form a working room in this impeller housing; One can be contained in the rotor on the driven shaft; An above-mentioned hydraulic servo device that thereby shift-in shifts out the bucket pipe that changes the flow rate that flows into the working oil in the working room and controls the position of bucket pipe in the working room.
Description of drawings
From the following explanation of accompanying drawing that the preferred embodiment of the present invention is shown in conjunction with example, can know and find out above-mentioned and other purposes, feature or advantage of the present invention.
Fig. 1 is the partial cross-sectional perspective view of the hydraulic servo device of first embodiment of the invention;
Fig. 2 A is a cross-sectional view, and one oil duct is communicated with the position relation between the oil duct when the axis of guide being shown being in one jiao of position with one;
Fig. 2 B is a cross-sectional view, and this oil duct is communicated with the position relation between the oil duct when the axis of guide being shown being in another position, angle with this;
Fig. 3 A is a cross-sectional view, and this oil duct is communicated with the position relation between the oil duct when the axis of guide being shown being in position, another angle with this;
Fig. 3 B is a cross-sectional view, the position that an oil duct is communicated with between the oil duct in the existing hydraulic servo device is shown concerns;
Fig. 4 illustrates the two-dimensional shape of this connection oil duct;
The angle range figure of Fig. 5 for fuel feeding oil duct and oil extraction oil duct with when being communicated with oil duct and interconnecting;
Fig. 6 is the longitudinal sectional drawing of the hydraulic servo device of second embodiment of the invention;
Fig. 7 is the longitudinal sectional drawing of the hydraulic servo device of third embodiment of the invention;
Fig. 8 is the longitudinal sectional drawing of the hydraulic servo device of fourth embodiment of the invention;
Fig. 9 is the longitudinal sectional drawing of the hydraulic servo device of fifth embodiment of the invention;
Figure 10 is the longitudinal sectional drawing of the hydraulic servo device of sixth embodiment of the invention;
Figure 11 is the sectional drawing of the hydrodynamic coupling of use one hydraulic servo device.
Embodiment
As shown in Figure 1, generally comprise that as the first embodiment of the invention hydraulic servo device of the actuator of the bucket pipe of hydrodynamic coupling shown in Figure 11 one is contained in the near-end of oil hydraulic cylinder 10, the axis of guide actuator that is connected with a controller (not shown) 12, one as the oil hydraulic cylinder 10, of high pressure resistant housing and stretches into the axis of guide 14 and a piston 16 in the space between the oil hydraulic cylinder 10 and the axis of guide 14 oil hydraulic cylinder 10 from axis of guide actuator 12.Piston 16 can be along the endwisely slipping of the axis of guide 14, but can't rotate around the axis of guide 14.Piston 16 comprises one near the large-diameter portion 18 of the near-end of oil hydraulic cylinder 10 and a minor diameter 20 near the far-end of oil hydraulic cylinder 10.The sliding eye 24 of the end wall 22 of minor diameter 20 from oil hydraulic cylinder 10 far-ends stretches out oil hydraulic cylinder 10 vertically.Minor diameter 20 is used to support the bucket pipe that is activated by this hydraulic servo device at its external part upper support a junction 26.
Piston 16 the separated by spaces in the oil hydraulic cylinder 10 become around among first space 28 of minor diameter 20 and the large-diameter portion 18 and on second space 30.Have in the far-end of oil hydraulic cylinder 10 one radially high pressure oil oil duct 32 be communicated with first space 28.One ring-shaped step 34 is arranged as a stop on the inner peripheral wall of oil hydraulic cylinder 10, prevent that piston 16 is moved further to the far-end of oil hydraulic cylinder 10 vertically.When oil hydraulic cylinder 10 was in this stop position, still there was first space 28 in the far-end of oil hydraulic cylinder 10, kept being communicated with first space 28 simultaneously.
Shown in Fig. 2 A, the axial center hole 36 and a pair of radially fuel feeding oil duct 38a, the 38b that stretches into this axial center hole 36 near large-diameter portion 18, from first space 28 that have an axis of guide 14 to slide therein in the minor diameter 20 of piston 16.Fuel feeding oil duct 38a, 38b roughly are symmetrical in the central axis of minor diameter 20.Also have a pair of plane, oil extraction oil duct 40a, the 40b parallel of central axis by minor diameter 20 that roughly be symmetrical in the minor diameter 20 with fuel feeding oil duct 38a, 38b.Oil extraction oil duct 40a, 40b are at joint 26 openings.Axial center hole 36 all is connected with an outside oil exit pipe (not shown) with oil extraction oil duct 40a, 40b.
There are a pair of connection oil duct 42a, 42b fuel feeding oil duct 38a, 38b to be communicated with second space 30 on the outer peripheral surface of the axis of guide 14 according to the position, angle of the axis of guide 14.Be communicated with the central axis that oil duct 42a, 42b roughly are symmetrical in the axis of guide 14.The length that each connection oil duct 42a, 42b stretch vertically is identical with the stroke of piston 16, and is the circumference that helical stretches the big half-turn axis of guide 14.In this embodiment, the diameter of fuel feeding oil duct 38a, 38b and oil extraction oil duct 40a, 40b equals to be communicated with the width of oil duct 42a, 42b.In Fig. 1,,, be communicated with one of oil duct 42a, 42b to be communicated with oil duct 42 expressions with one of oil extraction oil duct 40 expression oil extraction oil duct 40a, 40b with one of fuel feeding oil duct 38 expression fuel feeding oil duct 38a, 38b.
The compression area of piston 16 in first space 28 is cross sectional area poor of the cross sectional area of large-diameter portion 18 and minor diameter 20.The compression area of piston 16 in second space 30 is cross sectional area poor of the cross sectional area of large-diameter portion 18 and the axis of guide 14.Therefore, the compression area of piston 16 in second space 30 is greater than the compression area of piston 16 in first space 28.When being communicated with oil duct 42 and being communicated with the fuel feeding oil duct 38 and second space 30, it is identical with oil pressure in second space 30 that the working oil in the high-pressure oil duct 32 acts on first space 28, and piston 16 is vertically to the far-end of oil hydraulic cylinder 10, promptly move to end wall 22.Thereby when being communicated with oil duct 42 and being communicated with working oil oil pressure in the high-pressure oil duct 32 with the oil extraction oil duct 40 and second space 30 and only acting in first space 28, piston 16 is vertically to the near-end of oil hydraulic cylinder 10, promptly move to axis of guide actuator 12.
As shown in Figure 4, each is communicated with oil duct 42 and is scroll, so piston 16 moves a straight line stroke vertically along with an angular displacement of the axis of guide 14.The large-diameter portion 18 of piston 16 is hollow, therefore, even piston 16 moves to the near-end of oil hydraulic cylinder 10 vertically fully, is communicated with oil duct 42 and is not also covered by piston 16.
Shown in Fig. 2 A, 2B and 3A, fuel feeding oil duct 38a and its other oil extraction oil duct 40a draw closer together than fuel feeding oil duct 38b and its other oil extraction oil duct 40b.This position, angle relation between these oil ducts 38a, 40a and 38b, the 40b is guaranteed: when the axis of guide 14 during around its axial rotation, be communicated with oil duct 42a and begin to be communicated with oil duct 42b with fuel feeding oil duct 38a or oil extraction oil duct 40a time ratio overlapping or that is communicated with and begin morning time overlapping with fuel feeding oil duct 38b or oil extraction oil duct 40b or that be communicated with.Definitely say, as shown in Figure 5, when the axis of guide 14 rotated in 2 θ angle ranges around its axis, it was overlapping or be communicated with to be communicated with oil duct 42a and fuel feeding oil duct 38a or oil extraction oil duct 40a, wherein, thus θ is corresponding with the width of diameter oil duct 42a, the 42b of oil duct 38a, 38b, 40a, 40b.The axis of guide 14 makes connection oil duct 42b and fuel feeding oil duct 32b or oil extraction oil duct 40b 2 θ angle ranges hysteresis one overlapping or that be communicated be not more than the angle α of θ around its rotational.Therefore, the axis of guide 14 make around its rotational be communicated with oil duct 42a, 42b and fuel feeding oil duct 38a, 38b or oil extraction oil duct 40a, 40b is overlapping or the whole angular range that is communicated with is (2 θ+α).(2 θ+α) are communicated with overlapping or the angle range when being communicated with of oil duct 42 and a fuel feeding oil duct 38 or an oil extraction oil duct 40 greater than the axis of guide 14 in the existing hydraulic servo device shown in Fig. 3 B one to this angle range.Therefore, connection oil duct 42a, 42b and fuel feeding oil duct 38a, 38b or oil extraction oil duct 40a, the disconnected possibility of 40b reduce, thereby this hydraulic servo device is wayward malfunctioning.
The following describes the working condition of first embodiment's hydraulic servo device.When controller when axis of guide actuator 12 sends a signal, axis of guide actuator 12 makes the axis of guide 14 clockwise rotate with the direction of arrow shown in Fig. 2 B from the position that is communicated with oil duct 42a, 42b shown in Fig. 2 A and is not communicated with fuel feeding oil duct 38a, 38b or oil extraction oil duct 40a, 40b.Shown in Fig. 2 B, be communicated with oil duct 42a and begin to be communicated with fuel feeding oil duct 38a.High-pressure work oil begins from first space 28 through fuel feeding oil duct 38a and is communicated with oil duct 42a to flow into second space 30, and piston 16 is because the compression face product moment on piston 16 positive and negative two directions and moving to the far-end of oil hydraulic cylinder 10 vertically.Tilt owing to be communicated with the crestal line of the relative axis of guide 14 of oil duct 42a, be communicated with oil duct 42a and shown in Fig. 2 A, be not communicated with fuel feeding oil duct 38a once more, thereby the axial displacement of piston 16 stops.
Piston 16 moves to the far-end of oil hydraulic cylinder 10 once more when the axis of guide 14 further turns to position shown in Fig. 2 B.Like this, rotate continuously under the feedback control of the axis of guide 14 when detecting the axial position of piston 16, be positioned on the required axial position up to piston 16.
Even as the load on the piston 16 greatly to piston 16 can't move axially or piston 16 its axial displacement on position shown in Fig. 2 B too little, then controller sends a control signal to the axis of guide 14 and makes the axis of guide 14 further clockwise rotate position shown in Fig. 3 A.On this position, be communicated with oil duct 42a, 42b and be communicated with fuel feeding oil duct 38a, 38b respectively, make high-pressure work oil flow into second space 30 from first space 28 through fuel feeding oil duct 38a, 38b and connection oil duct 42a, 42b.Thereby driving force improves, responsiveness improves thereby the flow rate that makes piston 16 axially movable working oil improves.Even at controller further when axis of guide actuator 12 sends a signal, be communicated with oil duct 42a, 42b and also be difficult for not being communicated with, because the axis of guide 14 is being communicated with oil duct 42a, 42b and fuel feeding oil duct 38a, the angle range of angle range when only using a connection oil duct 42 and a fuel feeding oil duct 38 when 38b is communicated with fuel feeding oil duct 38a, 38b.
For piston 16 is moved to the near-end of oil hydraulic cylinder 10 vertically, the axis of guide 14 rotates from position shown in Fig. 2 A with the counter clockwise direction opposite with Fig. 2 B arrow.Be communicated with oil duct 42a and begin to be communicated with, thereby second space 30 is communicated with oil exit pipe with oil extraction oil duct 40a.Because the oil pressure in second space 30 descends, thus under the effect of the oil pressure of piston 16 in first space 28 vertically the near-end to oil hydraulic cylinder 10 move, be not communicated with shown in Fig. 2 A up to being communicated with oil duct 42a with oil extraction oil duct 40a.Rotate continuously under the feedback control of the axis of guide 14 when detecting the axial position of piston 16, thus the axial position of control piston 16.Because the relative position of oil extraction oil duct 40a, 40b is identical with fuel feeding oil duct 38a, 38b, so piston 16 responsiveness raising when the near-end of oil hydraulic cylinder 10 moves axially, be communicated with oil duct 42a, 42b and can be communicated with oil extraction oil duct 40a, 40b.
Fig. 6 illustrates the hydraulic servo device of second embodiment of the invention.In Fig. 6, a gas outlet 44 is connected with the top of the near-end of oil hydraulic cylinder 10, thereby is communicated with second space 30.Gas outlet 44 is communicated with atmosphere through a hole 46.The air that is trapped within the working oil of high-pressure oil duct in second space 30 can be discharged through gas outlet 44.Therefore, the responsiveness of this hydraulic servo device is not subjected to this harmful effect that is trapped air.Because there is a very little air hole in hole 46, but so its exhausting air and still keep oil pressure in second space 30.
Fig. 7 illustrates the hydraulic servo device of third embodiment of the invention.Hydraulic servo device shown in Figure 7 is the improvement to hydraulic servo device shown in Figure 6.Be connected with the top of the near-end of oil hydraulic cylinder 10 with the gas outlet 44 that atmosphere is communicated with by hole 46, and sliding eye 24 usefulness one oil storage tank 48 in the end wall 22 covers.This oil storage tank 48 is defined by the base plate 50 and the wall 52 that are contained on the end wall 22.There is a hole (not shown) to pass in the wall 52 for the bucket pipe that activates by this hydraulic servo device.The height of oil storage tank 48 preferably is equal to or greater than the height of the bottom of the gas outlet 44 that is connected with oil hydraulic cylinder 10.
In the embodiment shown in fig. 6, because gas outlet 44 46 is communicated with atmosphere through the hole, do not spill from the minor diameter 20 of piston 16 and the gap between the end wall 22 thereby therefore in this hydraulic servo device is not worked second space 30, there is oil pressure to make the pressure head that the time spent working oil understands owing to the working oil in second Room 30.Therefore, air can flow into second space 30 from gas outlet 44.This air can cause the job insecurity of hydraulic servo device or responsiveness to reduce when starting working next time.In the embodiment shown in fig. 7, the oil storage tank 48 that covers sliding eye 24 can prevent effectively that working oil from spilling from the gap between minor diameter 20 and the end wall 22, thereby this hydraulic servo device can stably or with required responsiveness be started working.
Fig. 8 illustrates the hydraulic servo device of fourth embodiment of the invention.Hydraulic servo device shown in Figure 8 also is the improvement to hydraulic servo device shown in Figure 6.In Fig. 8, gas outlet 44 and the connecting end of oil hydraulic cylinder 10 and hole 46 between a safety check 51 is arranged.Safety check 51 prevents that when this hydraulic servo device is not worked air from flowing in second space 30 through gas outlet 44.Safety check 51 can replace with remote control or automated switch valve, and this valve is only opened when needed.
Fig. 9 illustrates the hydraulic servo device of fifth embodiment of the invention.In Fig. 9, the bottom of oil hydraulic cylinder 10 inner peripheral surfaces has two dimples 56 to lay respectively at by the far-end and near-end of oil hydraulic cylinder 10 in first and second spaces 28,30.The particle that the inner peripheral surface that these two dimples 56 are used for collecting piston 16 relative oil hydraulic cylinders 10 is generated when sliding.Also have two tap holes 58 to be communicated with two dimples, 56 bottoms respectively in the cylindrical wall of oil hydraulic cylinder 10, thereby discharge the particle that is collected on two dimples, 56 bottoms.Two tap holes 58 clog with two oil-proof chock plugs 60 usually.Because the particle collection that is generated by the slip of the inner peripheral surface of piston 16 relative oil hydraulic cylinders 10 is in dimple 56, thereby so they be difficult for resting on the inner peripheral surface of oil hydraulic cylinder 10 and be difficult for being clipped between piston 16 and the oil hydraulic cylinder 10.Take out chock plug 60 and just can discharge particle, thus when hydraulic servo device does not use with cleaning solution cylinder pressure 10 inside such as work wet goods.
Figure 10 illustrates the hydraulic servo device of sixth embodiment of the invention.Hydraulic servo device shown in Figure 10 is designed to be convenient to maintenance.In Figure 10, on the end face of the large-diameter portion 18 of piston 16 tapped hole 64 is arranged,, from oil hydraulic cylinder 10, extracts the elongated shape screw rod 62 of piston stripping attachment piston 16 as screwing in these tapped holes 64.Behind working oil Extract cylinder pressure 10, unload lower end wall from the near-end of oil hydraulic cylinder 10, take out the axis of guide 14 then.Then elongated shape screw rod 62 is screwed in the tapped hole 64, from oil hydraulic cylinder 10, extract piston 16 vertically.Use elongated shape screw rod 62 to need not to take apart oil hydraulic cylinder 10 and just can from oil hydraulic cylinder 10, take out piston 16, therefore be convenient to workman's inspection, maintenance or replacing piston 16, oil hydraulic cylinder 10, be contained in the bucket pipe on the piston 16.
Although more than be shown specifically and illustrated preferred embodiments more of the present invention, should see, can make all changes and correction within the scope of the claims.
Claims (20)
1, a kind of hydraulic servo device is characterized in that, comprising:
One oil hydraulic cylinder;
One extends in the axis of guide of described oil hydraulic cylinder on axially rotationally, and a pair of connection oil duct is arranged on the outer peripheral surface of the described axis of guide;
One be contained in slidably on the described axis of guide and in described oil hydraulic cylinder axially movable piston, a pair of oil duct is arranged in the described piston;
One actuator, this actuator makes the described axis of guide around its rotational, thereby at least one described connection oil duct is communicated with at least one described oil duct, thereby the fluid of band pressure is acted on the described piston and described piston is axially moved in described oil hydraulic cylinder;
Described connection oil duct is arranged to the relative position of described oil duct: the angle range that causes an oil duct to be communicated with the axis of guide of oil duct connection with differs from one another with the angle range that causes another oil duct to be communicated with the axis of guide of oil duct connection with another.
2, by the described hydraulic servo device of claim 1, it is characterized in that the curved shape of each described connection oil duct.
By the described hydraulic servo device of claim 1, it is characterized in that 3, described oil duct is included in the fuel feeding oil duct and the oil extraction oil duct that is connected with an oil exit pipe of supply working oil under the pressure.
4, by the described hydraulic servo device of claim 1, it is characterized in that, the inner space of described oil hydraulic cylinder is separated into first space and second space by described piston, described first space is communicated with a high pressure oilhole, whether described second space is communicated with described oil duct by described connection oil duct selects, thereby this hydraulic servo device comprises that also one is connected the gas outlet with described second spatial communication with described oil hydraulic cylinder top.
By the described hydraulic servo device of claim 4, it is characterized in that 5, described gas outlet has an air outlet hole to be discharged in the atmosphere for air.
By the described hydraulic servo device of claim 4, it is characterized in that 6, described gas outlet has a safety check to be discharged in the atmosphere for air.
7, by the described hydraulic servo device of claim 1, it is characterized in that, the inner space of described oil hydraulic cylinder is separated into first space and second space by described piston, described first space is communicated with a high pressure oilhole, whether described second space is communicated with by described connection oil duct selection with described oil duct, described oil hydraulic cylinder has the dimple of collection particle wherein, and described dimple is arranged in described first space and/or this oil hydraulic cylinder inner peripheral surface bottom, described second space.
8, by the described hydraulic servo device of claim 7, it is characterized in that having a tap hole to discharge the particle that is collected in the described dimple in the cylindrical wall of described oil hydraulic cylinder.
9, by the described hydraulic servo device of claim 1, it is characterized in that, the inner space of described oil hydraulic cylinder is separated into first space and second space by described piston, described first space is communicated with a high pressure oilhole, whether described second space is communicated with by described connection oil duct selection with described oil duct, and this hydraulic servo device comprises that also one covers the oil storage tank of an end wall in described first space of defining of described oil hydraulic cylinder.
10, by the described hydraulic servo device of claim 1, it is characterized in that having connection set to be connected on the end face of described piston, so that from described oil hydraulic cylinder, pull out described piston with a piston stripping attachment.
11, a kind of hydrodynamic coupling is characterized in that, comprising:
Can be contained in an impeller and an impeller housing on the driving shaft, form a working room in the described impeller housing;
One can be contained in the rotor on the driven shaft;
Thereby one in described working room shift-in shift out the bucket pipe of the flow rate that change to flow into the working oil in the described working room; And
The hydraulic servo device of the position of the described bucket pipe of one control, described hydraulic servo device comprises:
One oil hydraulic cylinder;
One extends in the axis of guide of described oil hydraulic cylinder on axially rotationally, and a pair of connection oil duct is arranged on the outer peripheral surface of the described axis of guide;
One be contained in slidably on the described axis of guide and in described oil hydraulic cylinder axially movable piston, a pair of oil duct is arranged in the described piston;
One actuator, this actuator makes the described axis of guide around its rotational, thereby at least one described connection oil duct is communicated with at least one described oil duct, thereby the fluid of band pressure is acted on the described piston and described piston is axially moved in described oil hydraulic cylinder;
Described connection oil duct is arranged to the relative position of described oil duct: the angle range that causes an oil duct to be communicated with the axis of guide of oil duct connection with differs from one another with the angle range that causes another oil duct to be communicated with the axis of guide of oil duct connection with another.
12, by the described hydrodynamic coupling of claim 11, it is characterized in that the curved shape of each described connection oil duct.
By the described hydrodynamic coupling of claim 11, it is characterized in that 13, described oil duct comprises the fuel feeding oil duct and an oil extraction oil duct that is connected with an oil exit pipe of a supply high-pressure work oil.
14, by the described hydrodynamic coupling of claim 11, it is characterized in that, the inner space of described oil hydraulic cylinder is separated into first space and second space by described piston, described first space is communicated with a high pressure oilhole, whether described second space is communicated with described oil duct by described connection oil duct selects, thereby described hydraulic servo device comprises that also one is connected the gas outlet with described second spatial communication with described oil hydraulic cylinder top.
By the described hydrodynamic coupling of claim 14, it is characterized in that 15, described gas outlet has an air outlet hole to be discharged in the atmosphere for air.
By the described hydrodynamic coupling of claim 14, it is characterized in that 16, described gas outlet has a safety check to be discharged in the atmosphere for air.
17, by the described hydrodynamic coupling of claim 11, it is characterized in that, the inner space of described oil hydraulic cylinder is separated into first space and second space by described piston, described first space is communicated with a high pressure oilhole, whether described second space is communicated with by described connection oil duct selection with described oil duct, described oil hydraulic cylinder has the dimple of collection particle wherein, and described dimple lays respectively at this oil hydraulic cylinder inner peripheral surface bottom in described first space and/or described second space.
18, by the described hydrodynamic coupling of claim 17, it is characterized in that having a tap hole to discharge the particle that is collected in the described dimple in the cylindrical wall of described oil hydraulic cylinder.
19, by the described hydrodynamic coupling of claim 11, it is characterized in that, the inner space of described oil hydraulic cylinder is separated into first space and second space by described piston, described first space is communicated with a high pressure oilhole, whether described second space is communicated with by described connection oil duct selection with described oil duct, and described hydraulic servo device comprises that also one covers the oil storage tank of an end wall in described first space of defining of described oil hydraulic cylinder.
20, by the described hydrodynamic coupling of claim 11, it is characterized in that having connection set to be connected on the end face of described piston, so that from described oil hydraulic cylinder, pull out described piston with a piston stripping attachment.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP21800397A JP3494858B2 (en) | 1997-07-29 | 1997-07-29 | Hydraulic servo device |
| JP218003/97 | 1997-07-29 | ||
| JP218003/1997 | 1997-07-29 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1210208A CN1210208A (en) | 1999-03-10 |
| CN1124418C true CN1124418C (en) | 2003-10-15 |
Family
ID=16713111
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN98103096.3A Expired - Lifetime CN1124418C (en) | 1997-07-29 | 1998-07-29 | Hydraulic servo device |
Country Status (4)
| Country | Link |
|---|---|
| EP (1) | EP0894982B1 (en) |
| JP (1) | JP3494858B2 (en) |
| CN (1) | CN1124418C (en) |
| DE (1) | DE69820934T2 (en) |
Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US7249458B2 (en) * | 2005-07-22 | 2007-07-31 | Ashradn Holdings Ltd. | Self-contained hydraulic actuator system |
| EP2255123A4 (en) * | 2008-02-29 | 2014-01-22 | Cbe Global Holdings Inc | SYSTEM AND METHOD FOR SINGLE AXIS DRIVE |
| WO2010093412A2 (en) * | 2009-02-10 | 2010-08-19 | Cbe Global Holdings, Inc. | Non-linear actuator system and method |
| CN103029828B (en) * | 2012-12-11 | 2016-03-23 | 江西洪都航空工业集团有限责任公司 | A kind of Mechanical rotation actuator |
| GB2517459A (en) * | 2013-08-21 | 2015-02-25 | Airbus Uk Ltd | A hydraulic actuator arrangement |
| KR101888053B1 (en) * | 2016-12-02 | 2018-08-13 | 한국남부발전(주) | Large capacity fluid coupling having device for controlling oil pressure scoop tube |
Family Cites Families (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2874542A (en) * | 1943-04-21 | 1959-02-24 | Sperry Rand Corp | Motion reproducing mechanism |
| GB693504A (en) * | 1949-07-25 | 1953-07-01 | Boulton Aircraft Ltd | Improvements in and relating to servo systems |
| US2926635A (en) * | 1957-12-24 | 1960-03-01 | Clark Equipment Co | Power shifting mechanism |
| US3757640A (en) * | 1971-12-01 | 1973-09-11 | Avco Corp | Simplified follower servomechanism |
| US4245547A (en) * | 1977-10-31 | 1981-01-20 | Commercial Shearing, Inc. | Rotary to linear servo mechanisms |
| EP0088017B1 (en) * | 1982-02-26 | 1987-11-19 | COMPAGNIE PARISIENNE D'OUTILLAGE A AIR COMPRIME Société anonyme dite: | Hydraulic directional spool valve |
| JPS60256603A (en) * | 1984-06-01 | 1985-12-18 | Yukio Watanabe | Cylinder device |
| JPH0729313Y2 (en) * | 1990-10-18 | 1995-07-05 | 株式会社大金製作所 | Release device for pull type clutch |
| DE19537417C2 (en) * | 1995-10-07 | 1997-07-24 | Eurocopter Deutschland | Hydraulic actuator |
-
1997
- 1997-07-29 JP JP21800397A patent/JP3494858B2/en not_active Expired - Lifetime
-
1998
- 1998-07-28 DE DE69820934T patent/DE69820934T2/en not_active Expired - Lifetime
- 1998-07-28 EP EP98114115A patent/EP0894982B1/en not_active Expired - Lifetime
- 1998-07-29 CN CN98103096.3A patent/CN1124418C/en not_active Expired - Lifetime
Also Published As
| Publication number | Publication date |
|---|---|
| DE69820934T2 (en) | 2004-11-04 |
| JPH1144303A (en) | 1999-02-16 |
| DE69820934D1 (en) | 2004-02-12 |
| EP0894982A3 (en) | 2000-05-24 |
| JP3494858B2 (en) | 2004-02-09 |
| EP0894982B1 (en) | 2004-01-07 |
| EP0894982A2 (en) | 1999-02-03 |
| CN1210208A (en) | 1999-03-10 |
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| SE01 | Entry into force of request for substantive examination | ||
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Granted publication date: 20031015 |