CN85107656A - Rotary fluid energy conversion device - Google Patents
Rotary fluid energy conversion device Download PDFInfo
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- CN85107656A CN85107656A CN85107656.4A CN85107656A CN85107656A CN 85107656 A CN85107656 A CN 85107656A CN 85107656 A CN85107656 A CN 85107656A CN 85107656 A CN85107656 A CN 85107656A
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- 239000012530 fluid Substances 0.000 title claims abstract description 107
- 238000006243 chemical reaction Methods 0.000 title claims description 11
- 230000002706 hydrostatic effect Effects 0.000 claims abstract description 114
- 230000003068 static effect Effects 0.000 claims abstract description 13
- 230000000694 effects Effects 0.000 claims description 17
- 238000006073 displacement reaction Methods 0.000 claims description 14
- 238000002347 injection Methods 0.000 abstract description 2
- 239000007924 injection Substances 0.000 abstract description 2
- 230000009471 action Effects 0.000 description 22
- 230000014509 gene expression Effects 0.000 description 19
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- 230000007246 mechanism Effects 0.000 description 9
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 5
- 239000007788 liquid Substances 0.000 description 4
- 230000007935 neutral effect Effects 0.000 description 4
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- 230000015572 biosynthetic process Effects 0.000 description 3
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- 239000000314 lubricant Substances 0.000 description 2
- 238000003199 nucleic acid amplification method Methods 0.000 description 2
- 230000002093 peripheral effect Effects 0.000 description 2
- 230000001105 regulatory effect Effects 0.000 description 2
- 239000007921 spray Substances 0.000 description 2
- 230000007306 turnover Effects 0.000 description 2
- 238000009736 wetting Methods 0.000 description 2
- 230000005540 biological transmission Effects 0.000 description 1
- 230000000295 complement effect Effects 0.000 description 1
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 239000007789 gas Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
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- 230000000717 retained effect Effects 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
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Abstract
The invention is characterized in: follow the relative rotation of casing and torque ring, the volume that forms between piston and cylinder increase and decrease space, and constantly increase and the space that reduces forms the fluid flow route of connection respectively at volume; Fluid in above-mentioned each space is injected the fluid passage of the 1st and the 2nd hydrostatic support.Rely on the static pressure of the fluid that injects the 1st hydrostatic support and the hydrostatic pressure of injection the 2nd hydrostatic support, just can on the torque ring, produce couple around running shaft.The 1st hydrostatic support has several pressure depressions, by throttle nozzle the fluid of respective voids is diverted in the pressure depression.
Description
The invention relates to the rotary fluid energy conversion device that hydrostatic profile fluid pump or fluid motor use.
In this rotary energy transducer before, that is in hydrostatic profile rotary fluid pump or the motor, for the rotating force of input shaft distance being converted to the translational forces of piston and guiding valve etc., and the translational forces of piston etc. converted to the running torque of output shaft, must adopt mechanical devices such as cam mechanism and linkage mechanism.Therefore, in this mechanism, because effects such as very strong extruding force and warping force are arranged between each parts, so, bearing is indispensable, and bearing depends on the viscosity of oiliness of lubricant oil and the immersional wetting of the oil film that forms, perhaps depends on the rolling action of ball and roller.Therefore, must be with wet goods working fluid with suitable viscosity.That is to say that because the near working fluid of water or viscosity and water is difficult to turn round sleekly, and service life of a machine is very short, so the kind of the working fluid that can use is restricted.In addition, use the mechanism of ball bearing, because the life-span of entire machine is decided by the fatigue life of this bearing, so be difficult to improve durability, and the volume ratio of ball bearing is bigger, and machine also is difficult to accomplish miniaturization and lighting.
Therefore, it is different fully with before technology starting point to have developed a kind of high efficiency fluid energy conversion device near perfect condition (opening clear and 58-77179 communique referring to the spy) recently.The structure of this transducer comprises: internal surface is the casing and the torque ring of conical surface, and this torque ring is by chimeric at spaced the 1st hydrostatic support of circumferencial direction and above-mentioned casing conical surface, and its inside is the inner plane that adapts with above-mentioned the 1st hydrostatic support; Several pistons in the internal arrangement of above-mentioned torque ring, make the end face of their fronts divide each inner plane of other torque ring closely to contact by the 2nd hydrostatic support; The cylinder that keeps the side of each piston head to slide, and supporting cylinder and the pivot that enables to rotate, pivot assemble to such an extent that depart from the axle center of said machine casing; Follow the relative rotation of said machine casing and torque ring, the space of the volume that between above-mentioned piston and said cylinder, forms increase and decrease, and, form the fluid flow route that is communicated with respectively in space and the ever-reduced space of volume that volume constantly increases; Fluid in above-mentioned each space is injected the fluid passage of the 1st and the 2nd hydrostatic support.Rely on the static pressure of the fluid that injects above-mentioned the 1st hydrostatic support and the static pressure of the fluid that injects above-mentioned the 2nd hydrostatic support, on above-mentioned torque ring, produce couple around running shaft.
But because the 1st hydrostatic support has single pressure depression respectively, and the centre-of-pressure position of each hydrostatic support is certain, so on above-mentioned torque ring, also have except the existence of the couple around the running shaft direction.That is to say, shown in the 11st and 12 figure, in this mechanism, the line of action La of the power Fa that produces by the static pressure of above-mentioned the 1st hydrostatic support a, pressure center (place-centric) b by this supporting a focuses on 1 d on the axle center m of said machine casing c and above-mentioned torque ring k, in other words the line of action Lb of the power Fb that is produced by the static pressure of the 2nd hydrostatic support e, is exactly that the center line g of piston f focuses on 1 i on the axle center n of above-mentioned pivot h.Therefore, although in order to produce the couple around running shaft on torque ring k, the internal surface of casing c must be subjected to displacement to the g of conical surface shape and the sense of rotation x of above-mentioned pressure center b, but the axial displacement of y is only the reason that causes above-mentioned torque ring bending or apply warping force.Therefore, the feature of this mode is durable in use, and can be slick and sly and high efficiency running.
Purpose of the present invention is intended to suppress effectively cause the couple beyond running shaft on the torque ring because depart from axial at the pressure center and the piston center of the 1st hydrostatic support, and the structure complicated of causing therefrom.
In order to achieve the above object, the 1st invention of the present invention is characterised in that: in having the fluid energy conversion device of above-mentioned the sort of special basic structure, each the 1st hydrostatic support made have a pair of pressure depression, the fluid of respective voids is diverted to above-mentioned each pressure depression by the throttling nozzle in the axle direction adjacency.
In addition, the 2nd invention is characterised in that: have several pressure depressions of axle direction adjacency except above-mentioned each the 1st hydrostatic support is made, also utilize the effect of above-mentioned piston and torque ring in axial relative displacement, be provided with the sliding sleeve that to supply with fluid selectively to above-mentioned each pressure depression, so that the center of the pressure center of above-mentioned the 1st hydrostatic support and above-mentioned piston reduced in axial departing from as far as possible.
According to the 1st invention, at the center of piston when the place-centric of the 1st hydrostatic support axially is subjected to displacement, because hydrodynamic pressure causes the amount of deflection effect of torque ring, this supporting is also bigger than the fluid leak-off gap near one side from the fluid leak-off gap on above-mentioned piston one side far away, so the pressure in the pressure depression on above-mentioned piston one side far away is lower than the pressure in the pressure depression near one side.As a result, the pressure center of the 1st hydrostatic support than place-centric to piston move on one side more, thereby above-mentioned pressure center and above-mentioned piston center just can be automatically to reducing adjustment in direction in axial departing from.
According to the 2nd invention, at the piston center when the place-centric of the 1st hydrostatic support axially is subjected to displacement, because the switching effect of sliding sleeve, can cut off to specific pressure depression supply pressure fluid, therefore, the pressure center of the 1st hydrostatic support just than place-centric to piston move on one side more.As a result, above-mentioned pressure center and above-mentioned piston center just can be automatically to reducing adjustment in direction in axial departing from.
Below, with reference to accompanying drawing one embodiment of the present of invention are described.The formation of the 1st invention at first, is described.
By several the 1st hydrostatic supports 3 torque ring 2 is embedded on the interior week of casing 1 rotationally, casing 1 is the cone shape member in the end that an end has open part 1a, at its interior all directions that embeds the position formation of above-mentioned torque ring 2 along open part 1a, the swedged gradually conical surface 4.In addition, torque ring 2 is members of annular, it has the perisporium 2a as the above-mentioned conical surface 4 identical cone angles, turning axle 6 is integrally outstanding to be installed on its end axial portions, it is by above-mentioned opening portion 1a, and the front end of this turning axle 6 leans on the outside of casing 1, and, on the position of each the 1st hydrostatic support 3 of respective torque ring 2 inboards, be provided with level and smooth inner plane 2c respectively.Again, the 1st hydrostatic support 3 is on the needed position of the periphery of torque ring 2, make splicing with shell 1 plane of inclination 4 on slide rail 5 tighten up, on this slide rail 5, form simultaneously several pressure depressions 7, and make hydrodynamic pressure import to 7 li of each pressure depressions.And number is that the hydrostatic support 3 of odd number is arranged by the equal angular compartment of terrain along circumference.And, the 5a of encirclement portion, 5b, 5c surround two pressure depression 7a, the 7b of above-mentioned slide rail 5, these encirclement portions are illustrated on Fig. 5 to Fig. 7, and the section of this slide rail 5 is in the shape that forms the chevron top by the above-mentioned conical surface 4 directions, thereby the slide area between the slide rail 5 and the conical surface 4 diminishes.And the above-mentioned encirclement 5a of portion, 5b, 5c can not form the parallel in shape with gyratory directions x.Specifically, have only the encirclement portion 5a vertical with gyratory directions to form straight line shape, the above-mentioned encirclement 5b of portion forms
"＜
"Font, again, the above-mentioned encirclement 5c of portion forms zigzag fashion.In addition, in the interior week of square ring 2, corresponding above-mentioned each the 1st hydrostatic support position forms inner plane 2c.Correspondingly in torque ring 2, on the position of each inner plane 2c in week, arrange several pistons 8 respectively, the fore-end 8a of these pistons 8 is spliced respectively by on the corresponding inner plane 2c of the 2nd hydrostatic support 9.The 2nd hydrostatic support 9 is to make planely, and the front-end face 8a of piston 8 closely is connected on the inner plane 2c, forms pressure depression 11 simultaneously on this front-end face 8a, and fluid is pressed import in the pressure depression 11.In addition, inboard at above-mentioned torque ring 2, adorning and making sliding parts 14a be supported in the pivot 14 on the casing 1 and rabbet ring-type cylinder barrel 15 on pivot 14 peripheries pivotally, this sliding parts has the axle center n that the axle center m with above-mentioned casing 1 parallels, on cylinder barrel 15, have some cylinders 16 along the circumferential direction the equal angles compartment of terrain, become radially to arrange.The axle center of these cylinders 16 almost becomes plumbness with the outer circumferential face of pivot 14.And, in each cylinder 16, can embed above-mentioned piston 8 with being free to slide, the inner face by the cardinal extremity face 8b of these pistons 8 and above-mentioned each cylinder 16 forms for fluid and flows to the space 13 of flowing out usefulness.Above-mentioned cylinder barrel 15 is connected on the above-mentioned torque ring 2 by Oldham's coupling 20 grades, turns round together with unequal angular velocity and this torque ring 2.Pivot 14 is Frusto-conical, and its outer circumferential face is the almost equal conical surface made from the perisporium 2a of above-mentioned torque ring 2 of cone angle, each above-mentioned piston 8 be retained with the perpendicular direction of perisporium 2a of torque ring 2 on can advance and retreat.And the sliding parts 14a of pivot 14 makes the lengthwise bulk that the transverse section is a stepped shape, and makes in its stepped shape groove 19 that is entrenched in casing 1 inside slidably.That is, this pivot 14 remain on slidably with the perpendicular direction of the axle center m of casing 1 on, thus, just can be regulated ， And to the space D of the axle center m of the axle center n of this pivot 14 and above-mentioned casing 1 and may be adjusted to and comprise zero desired numerical value.And and, shown in the 2nd figure, with the corresponding to imaginary cutting lines P of glide direction of above-mentioned pivot 14 as the boundary line, the inside of above-mentioned casing 1 is divided into the 1st field A and the 2nd field B two-part, make by the above-mentioned space 13 in the 1st above-mentioned field A all to be communicated in the passage 21 of the 1st fluid flow, make simultaneously by the above-mentioned space 13 in the 2nd field B all to be communicated on the 2nd fluid passage 22.The 1st fluid passage 21 possesses cylinder port 23, and pivot openings 24 and fluid flow out inflow entrance 25, and above-mentioned cylinder port 23 is to make each above-mentioned space 13 openings on inner peripheral surface (valve face) 15V of cylinder barrel 15.And pivot through hole 24 be an end opening on the A side, the 1st field of outer circumferential face (valve face) 14V of pivot 14, the other end opening is on the 2nd field B skew back face 14b of pivot 14 and sliding parts 14a.It is that the other end with pivot through hole 24 is opened on the casing 1 accordingly that above-mentioned fluid flows out 25 of inflow entrances.And, end place at pivot through hole 24, between inner peripheral surface (valve face) 15V of outer circumferential face (valve face) 14V of pivot 14 and cylinder barrel 15, installing forms the pressure depression (hole of turnover usefulness) 27 of the 3rd hydrostatic support 26, on the other end, installing forms the pressure depression 29 of the 4th hydrostatic support 28 between the inner face of the inclined-plane of pivot 14 14b and casing 1 simultaneously.Above-mentioned pressure depression 27 is elongated in a circumferential direction, also played to make and be present in the space 13 that can have on the 1st field A, be communicated to the effect on the pivot through hole 24, and pressure depression 29 is elongated on the glide direction of pivot 14, plays to prevent from pivot through hole 24 and fluid are flow to the cut effect of connection between the mouth 25 when this pivot 14 is slided.On the other hand, the 2nd fluid passage 22 possesses above-mentioned fluid passage 23 and pivot through hole 34 and fluid and flows to mouth 35, above-mentioned pivot through hole 34 be an end opening on the B side, the 2nd field of outer circumferential face (valve face) 14V of pivot 14, and the other end opening is on the 1st field A skew back face 14c of the sliding parts 14a of pivot 14.It is that the other end with pivot through hole 34 correspondingly is opened on the casing 1 that above-mentioned fluid flows to mouthfuls 35.And, on an end of pivot through hole 34, installing forms the pressure depression (hole of turnover usefulness) 77 of the 3rd hydrostatic support 36 between pivot 14 and cylinder barrel 15, on the other end, installing forms the pressure depression 39 of the 4th hydrostatic support 38 between the inner face of the inclined-plane of pivot 14 14c and casing 1 simultaneously.The structure of these depressions 37,39 and above-mentioned pressure depression the 27, the 29th, same.
In such structure, import path 41 with hydrodynamic pressure in each piston 8 corresponding spaces 13 by the pressure that is located at these piston 8 axial portions and import in the pressure depression 11 of corresponding the 2nd hydrostatic support 9, the hydrodynamic pressure in this pressure depression 11 imports 7 li of the pressure depressions of corresponding the 1st hydrostatic support 3 by being opened in fluid passage 42 on the torque ring 2 simultaneously.And, the direction and the area of two above-mentioned hydrostatic supports 3,9 are decided to be such numerical value, promptly by the action of hydrostatic pressure that imports the 1st hydrostatic support 3 in the power on the torque ring 2 with by the power of action of hydrostatic pressure on torque ring 2 that imports the 2nd hydrostatic support 9, equal and opposite in direction and direction is opposite.Again, the face of the 2nd hydrostatic support 9 is decided to be such numerical value, promptly by the action of hydrostatic pressure that imports this hydrostatic support 9 on piston 8 power and cancel out each other by the power of the action of hydrostatic pressure in the space 13 on piston 8.And, the 3rd hydrostatic support 26(36) area is decided to be such value, promptly by importing this hydrostatic support 26(36) hydrostatic pressure of lining on cylinder barrel 15 power and by being present in corresponding field A(B) the power of action of hydrostatic pressure on cylinder barrel 15 in the space 13 of lining cancels out each other.And above-mentioned the 4th hydrostatic support 28(38) and at this hydrostatic support 28(38) go up set inclined-plane 14b(14c) the angle of inclination be decided to be such value, promptly by importing this hydrostatic support 28(38) action of hydrostatic pressure of lining is in the power on the pivot 14 with by importing to and inclined-plane 14b(14c) corresponding field A(B) and the lining exist the 3rd support 26(36) power of action of hydrostatic pressure on pivot 14 of lining cancels out each other.
The following describes the action of illustrated embodiment.
At first, when using, high-pressure liquid is passed through for example the 1st fluid passage line 21, supply with the space 13 that exists among the 1st field A as fluid motor ... in.Then, as shown in the figure, make the axle center m of the relative casing 1 of axle center n of pivot 14 only depart from needed space D.So, shown in the 4th figure, in above-mentioned the 1st field,, compare with the line of action that acts on the power Fb on the above-mentioned torque ring 2 that causes by the static pressure that injects the fluid in the 2nd hydrostatic support 9 by the line of action that acts on the power Fa on the torque ring 2 that the static pressure that injects the fluid in the 1st hydrostatic support 3 causes, x has been offset to sense of rotation, so, above-mentioned directed force F a and Fb equal and opposite in direction, direction is opposite, two power of the formation effect of being parallel to each other, that is form couple.But shown in the 4th figure, several local couple Fa that takes place on torque ring 2 and the effect of Fb make above-mentioned torque ring 2 rotate towards same direction respectively.Therefore, above-mentioned torque ring 2 directly is subjected to the effect from the couple Fa and the Fb of fluid, rotates to arrow S direction.That is to say that under the situation of illustrated embodiment, the size of supposing above-mentioned each couple Fa and Fb is F, the distance of line of action is l
1, l
2, l
3, the moment M that then acts on the above-mentioned torque ring 2 is M=F(l
1+ l
2+ l
3), under the effect of this moment, the just relative casing 1 of above-mentioned torque ring 2 rotates.At this moment, rotation along with above-mentioned torque ring 2, space 13 in the 1st field A ... volume increase gradually, and the space 13 in the 2nd field B ... volume reduce gradually, so high-pressure liquid little by little flows into the space 13 of running through the 1st field A just by the 1st fluid flow route 21 ... in, the later fluid of work done is the space 13 from running through the 2nd field B then ... by the 2nd fluid flow route 22, little by little discharge outside the casing 1.In addition, if above-mentioned pivot 14 is slided into its axle center n neutral position consistent with the axle center m of said machine casing 1 from this state since between the line of action of above-mentioned directed force F a and Fb apart from l
1, l
2, l
3Vanishing respectively is so the moment that acts on the above-mentioned torque ring 2 disappears, so output equals zero thereupon.In addition, if make above-mentioned pivot 14 cross the neutral position, along with the direction opposite skew with illustrated embodiment, so, between the line of action of above-mentioned couple Fa and Fb apart from l
1, l
2, l
3Become negative value respectively, so, the just rotation in the opposite direction of above-mentioned torque ring 2.
On the other hand, when using, rely on external force to drive, make above-mentioned torque ring 2 towards for example arrow R direction rotation as fluid pump.So, under the situation of illustrated embodiment, on torque ring 2, producing and above-mentioned identical couple Fa and Fb, these couples Fa and Fb and the input torque that is added on the torque ring 2 balance each other.In addition, the fluid of casing 1 outside by the 2nd fluid flow route 22, little by little is inhaled into the space 13 of running through the 2nd field B ... in, pressure increases later fluid, from the space 13 of running through the 1st field A ... spray outside the casing 1 by pursuing ground by the 1st fluid flow route 21.If above-mentioned pivot 14 is slided into the neutral position, the spray volume vanishing of fluid, under the state that keeps static balance, 2 idle running of torque ring.If make above-mentioned pivot 14 cross the neutral position,, so, occur in the 2nd field with the couple Fa and the Fb of input torque balance, so high-pressure liquid is just by outside the 2nd fluid flow route 22 ejection casings 1 towards the direction opposite skew with illustrated embodiment.
But, no matter situation as the motor use, or situation as the pump use, as previously mentioned, along with the relative rotation of said machine casing 1 with above-mentioned torque ring 2, though the place-centric b of above-mentioned the 1st hydrostatic support 3 and the center g of above-mentioned piston 8 also are subjected to displacement to the y axle direction, but, because this fluid energy conversion device is made above-mentioned the 1st hydrostatic support 3 and is had a pair of pressure depression 7a and 7b in the axle direction adjacency, and the fluids in the corresponding space 13 are diverted in above-mentioned each pressure depression 7a and the 7b by throttling nozzle 40a and 40b, so, can access the effect shown in the 8th figure～the 10th figure.That is to say, shown in the 8th figure, under the center g state that axle direction does not depart from outside of the place-centric b of the 1st hydrostatic support 3 and piston 8, pressure in two pressure depression 7a and the 7b equates, therefore, because the hydrostatic pressure of above-mentioned supporting 3, point of action (pressure center) q that acts on the power Fa on the above-mentioned torque ring 2 does not have position deviation with the center g of piston 8 in Y direction.On the other hand, shown in the 9th figure, as the center of piston 8 g, from the place-centric b of the 1st hydrostatic support 3 when the axial displacement, because fluid is pressed the amount of deflection effect of the perisporium 2a of the torque ring 2 cause, this supporting 3 is bigger than the fluid leak-off gap 46a near one side from the fluid leak-off gap 46b on above-mentioned piston 8 one side far away.So the pressure in the pressure depression 7b on above-mentioned piston 8 one side far away is also low than the pressure in the pressure depression 7a near one side.As a result, the pressure center q of the 1st hydrostatic support 3 than place-centric b to piston 8 move on one side more, so the center g of above-mentioned pressure center q and piston 8 can be automatically to reducing adjustment in direction in departing from of axis direction.In addition, when situation about becoming from this state Rotate 180 degree shown in the 10th figure, that is the center g of piston 8, from the place-centric b of the 1st hydrostatic support 3 at axle direction towards when opposite just now direction moves, because fluid is pressed the amount of deflection effect of the perisporium 2a of the torque ring 2 that causes, this torque ring 2 is from the fluid leak-off gap 46a on above-mentioned piston 8 one side far away, and is bigger than the fluid leak-off gap 46b near one side.So, the pressure in the pressure depression 7a on above-mentioned piston 8 one side far away is also low than the pressure in the pressure depression 7b near one side.As a result, the pressure center q of the 1st hydrostatic support 3 than place-centric b to piston 8 move on one side more, at this moment, the center g of above-mentioned pressure center q and above-mentioned piston 8 also can be automatically to reducing adjustment in direction in axial departing from.
As mentioned above, rotary fluid energy conversion device of the present invention, can be used as fluid pump or fluid motor uses, but, no matter which kind of situation, all be only by injecting the 1st hydrostatic support 3 ... with the 2nd hydrostatic support 9 ... the static pressure of fluid on torque ring 2, produce couple Fa and Fb, and this couple Fa and Fb and the input torque or the output torque that act on this torque ring 2 balance each other.That is to say, such mechanism can directly only be converted to the static pressure of fluid the running torque of torque ring 2, and, also can be directly the running torque of above-mentioned torque ring 2, be converted to the pressure of fluid, all mechanical devices that translational forces and running torque carried out mechanical switch do not need.As previously mentioned, can be suppressed to inferior limit to the pressure center of above-mentioned the 1st hydrostatic support and above-mentioned piston center in axial departing from, thereby prevent that bending moment and torsional moment etc. affact on the above-mentioned torque ring improperly.
Secondly, the 2nd invention is described.The 2nd invention also having feature aspect the slide rail of hydrostatic support, because rotary energy switching mechanism is identical, and its structure and working procedure, the front was introduced in detail, omitted here.Below, be the center with slide rail as feature of the present invention.The 13rd figure to the 15 figure are described.
In these figure, the structure of the 1st hydrostatic support 3 is the slide rails 5 that closely contact with the conical surface 4 of said machine casing 1, be fixed on the necessary place of periphery of above-mentioned torque ring 2, simultaneously, three pressure depression 7a, 7b, 7c axially with these slide rail 5 adjacency so that the fluid pressure injection is gone in each pressure depression 7a, 7b and the 7c.And, odd number hydrostatic support 3 ... along the circumferential direction assemble at interval by equal angles.In addition, shown in the 5th figure～the 7th figure, the section of encirclement part 5a, 5b, 5c, 5d and 5e that above-mentioned slide rail 5 is surrounded pressure depression 7a, 7b and 7c, being along the direction of the above-mentioned conical surface 4 has the mountain on mountain peak word shape, thereby, this slide rail 5 and the slide area of the above-mentioned conical surface 4 are reduced.And above-mentioned encirclement part 5a, 5b, 5c, 5d and 5e form and the uneven shape of sense of rotation x.Particularly, form rectilinear form though have only with the encirclement part 5a of sense of rotation X quadrature and 5b,, above-mentioned encirclement part 5C and 5e but form "＜" word shape, and the relative sense of rotation x of above-mentioned encirclement part 5d becomes skewed.
In such mechanism, import path 41 by the pressure on the axle center that is arranged on piston 8, fluid in the space 13 corresponding with above-mentioned each piston 8 is pressed, import in the pressure depression 11 of corresponding the 2nd hydrostatic support 9, simultaneously, by running through fluid passage 42a, 42b and the 42c of above-mentioned torque ring 2, the fluid in this pressure depression 11 is pressed, import in pressure depression 7a, the 7b and 7c of corresponding the 1st hydrostatic support 3.And, by these fluid passages 42a, 42b, 42c and above-mentioned pressure depression, constitute sliding sleeve part 50.Shown in the 8th figure to the 10 figure, because this sliding sleeve 50 has utilized above-mentioned piston 8 and the relative displacement of above-mentioned torque ring 2 in Y direction, can be selectively, intermittently to above-mentioned each pressure depression 7a, 7b and 7c supply with fluid, so, as the place-centric b of the 1st hydrostatic support 3 and the center g of piston 8, when departing from of Y direction is in certain scope, though above-mentioned pressure depression 11 and all fluid passage 42a, 42b, 42c is communicated with, but, center g when above-mentioned place-centric b and above-mentioned piston 8, when axial position deviation surpasses certain scope, shown in the 9th figure or the 10th figure, fluid passage 42c or 42a from above-mentioned piston 8 one side far away were spaced with being communicated with of above-mentioned pressure depression 11.In addition,, assembling separately throttling nozzle 40a, 40b and 40c respectively at above-mentioned fluid passage 42a and 42b midway.
As previously mentioned, no matter situation as the motor use, or situation as the pump use, follow the relative rotation of said machine casing 1 and above-mentioned torque ring 2, though the place-centric b of above-mentioned the 1st hydrostatic support 3 and the center g of above-mentioned piston 8, all be subjected to displacement to Y direction, but, because this fluid energy conversion device is made the 1st hydrostatic support 3 and is had several pressure depression 7a, the structure of 7b and 7c, these pressure depressions are adjacency axially, simultaneously, also be provided with sliding sleeve 50, this sliding sleeve 50 utilizes above-mentioned piston 8 and above-mentioned torque ring 2, relative displacement in Y direction, can be selectively, intermittently to above-mentioned each pressure depression 7a, 7b and 7c supply with fluid, so, can access the effect shown in the 8th figure～the 10th figure.That is to say, shown in the 8th figure, at the place-centric b of the 1st hydrostatic support 3 and the center g of piston 8, under the state that Y direction does not depart from, because all fluid passage 42a, 42b and 42c are communicated with pressure depression 11, so, each pressure depression 7a, pressure in 7b and the 7c all equates, therefore, because the hydrostatic pressure of above-mentioned the 1st hydrostatic support 3, act on point of action (pressure center) q of the power Fa on the above-mentioned continuous square ring 2 and the center g of above-mentioned piston 8 and all do not have position deviation in Y direction, in addition, in that the center of piston 8 g is little along the position deviation of Y direction and under near the state that displacement directions X is big (among the 12nd figure t and u), because fluid passage 42a and 42c are cut off from pressure depression 11, have only fluid passage 42b to be communicated with pressure depression 11, so, act on point of action (pressure center) q of the power Fa on the torque ring 2 and the center g of piston 8, all very little at axial position deviation.On the other hand, shown in the 9th figure, when the center of piston 8 g from the place-centric b of the 1st hydrostatic support 3 during to the Y direction occurrence positions, fluid passage 42c and above-mentioned pressure depression from above-mentioned piston 8 one side far away separate.Therefore, the 1st hydrostatic support 3 can only be to two pressure depression 7a and the 7b supply pressure fluid near piston 8.As a result, the pressure center g of the 1st hydrostatic support 3 than place-centric b to piston 8 move on one side more, so the center g of above-mentioned pressure center q and above-mentioned piston 8 can be automatically to reducing adjustment in direction in departing from of axis direction.In addition, when this state Rotate 180 is spent, the situation shown in the 10th figure, that is, when the center g of piston 8 from the place-centric b of the 1st hydrostatic support 3 at axle direction during with opposite just now direction displacement, fluid passage 42a and above-mentioned pressure depression 11 from above-mentioned piston 8 one side far away separate.Therefore, 3 of the 1st hydrostatic supports are to two pressure depression 7b and 7c supply pressure fluid near piston 8.As a result, the pressure center q of the 1st hydrostatic support 3 than place-centric b to piston 8 move on one side more, so the center q of at this moment above-mentioned pressure center q and above-mentioned piston 8 can both be automatically to reducing adjustment in direction in departing from of axis direction.In addition, at fluid passage 42c(or 42a) the firm state that disconnects, that is the also not too big stage of the displacement amount of the axle center g of the place-centric b of hydrostatic support 3 and piston 8, though pressure center q might occur also will be a little further from above-mentioned place-centric b than the center g of piston 8, but, in case pressure center q surpasses the center g of piston 8, b departs to Y direction from place-centric, so, because the amount of deflection effect on the perisporium 2a of above-mentioned torque ring 2, the fluid leak-off gap 45c(or the 45a on one side that above-mentioned pressure center q moved) will increase a bit, and the pressure depression 7a(or the 7b on one side that moved the pressure center) in pressure reduce a bit.Therefore, above-mentioned pressure center q can be to the adjustment in direction position near the center q of above-mentioned piston 8.In addition, in the 8th figure～the 10th figure, Fa, Fb, Fc have schematically represented the power on the above-mentioned torque ring 3 of acting on that causes owing to the pressure in above-mentioned each pressure depression 7a, 7b and the 7c.
As previously mentioned, can be suppressed to inferior limit to the pressure center of above-mentioned the 1st hydrostatic support and above-mentioned piston center in axial departing from, thereby prevent that bending moment and torsional moment etc. affact on the above-mentioned torque ring improperly.
Therefore, making does not have the structure of effects such as strong extruding force and warping force to accomplish easily between each parts, and, it also is possible not using the bearing part of the rolling action of parts such as relying on bearing, ball and roller fully, and these parts all depend on the oiliness of lubricant oil and viscosity and the immersional wetting of the oil film that forms.That is to say, such structure can all constitute the sliding parts of each parts with hydrostatic support, the fluid near as working fluid, water or viscosity and water can both use, without any disadvantageous place, in addition, if replace rolling bearing with hydrostatic support, so, owing to be not subjected to the age limit of rolling bearing, so, machine can use for a long time, and can make machine accomplish that volume is little, in light weight.
As above-mentioned embodiment, if can regulate the eccentric position of the relative casing of pivot, so, and just can be easily as the pump or the motor use of volume-variable formula, still, the present invention might not be limited to such situation.
In addition, even under the situation that the eccentric position of above-mentioned pivot can be regulated, mean of calculating also is not limited to above the introduction, for example: can utilize fluid to press transmission device, make various distortion such as above-mentioned pivot is reciprocating.
And then, surround the encirclement part of the pressure depression of the 1st hydrostatic support, certainly also be not limited to the section shape of above introduction, still, if introduce as top, make the shape of mountain i section, so,, this forms the wedge-shaped cross section space, so during work because surrounding between part and the conical surface part, fluid injects this wedge shape space, can produce dynamics pressure.Therefore, casing can carry out more sleekly with the relative rotation of torque ring.In addition, if the shape that does not have parallel portion with sense of rotation is partly made in above-mentioned encirclement, so, because the said dynamics pressure in front all takes place in all places of above-mentioned encirclement part, so, can obtain at a high speed and good especially supporting role.In addition, obviously can make parts to torque ring 2 and slide rail 5, make the complementary angle of the semiapex angle of the mountain i section that surrounds part greater than the conical surface drift angle of torque ring periphery, for example, when torque ring 2 and slide rail 5 usefulness foundry goods are made parts, the mold of torque ring periphery can be sloughed along axial direction, so, can enhance productivity.In other words, make the gradient of the mountain i section of above-mentioned encirclement part,, can be easy to molding greater than the gradient of casing inner conical face.
In addition, the number of piston also is not limited to the quantity that illustrated embodiment is drawn.
At last, working body is not limited to liquid such as oil or water, for example: also can be gases such as air.
Because the present invention is top such mechanism, so, the rotary fluid energy conversion device that can provide is characterised in that: can not use all mechanical devices that translational forces and rotating force carried out mechanical switch, and the performance of performance pump formula or motor, and can not adopt parts such as a cutting valve, rely on simple structure, just can suppress effectively owing to the pressure center of the 1st hydrostatic support and piston center in the axial couple beyond running shaft on the torque ring that acts on that produces that departs from.
Being simply described as follows of drawing:
Fig. 1 to Figure 10 is expression the 1st inventive embodiment of the present invention, Fig. 1 is an orthogonal view, Fig. 2 is the II-II sectional drawing on Fig. 1, Fig. 3 is the III-III sectional drawing on Fig. 1, Fig. 4 is the IV-IV sectional drawing on Fig. 3, and Fig. 5 is the amplification view of the pressure pocket recess of the 1st hydrostatic support on the presentation graphs 1, and Fig. 6 is the VI-VI sectional drawing on Fig. 5, Fig. 7 is the VII-VII sectional drawing of presentation graphs 5, and Fig. 8 to Figure 10 is the Action Specification figure of the 1st inventive embodiment.Figure 11 is expression prior art embodiment's the 1st a hydrostatic support partial plan layout.
Figure 13 to Figure 22 represents the 2nd inventive embodiment of the present invention, Figure 13 is an orthogonal view, Figure 14 is the II-II sectional drawing on Figure 13, Figure 15 is the III-III sectional drawing on Figure 13, Figure 16 is the IV-IV sectional drawing on Figure 15, and Figure 17 is the amplification view of the pressure pocket recess of the 1st hydrostatic support on expression Figure 13, and Figure 18 is the VI-VI sectional drawing on Figure 17, Figure 19 is the stereogram of expression pressure pocket recess shown in Figure 17, and Figure 20 to Figure 22 is the Action Specification figure of the 2nd inventive embodiment.Figure 23 is expression prior art embodiment's a part sectioned view, and Figure 24 is expression prior art embodiment's the 1st a hydrostatic support partial plan layout.In addition, Figure 25 represents other embodiment's of the present invention explanatory drawing.
1 expression casing
2 expression torque rings
2c represents inner plane
3 expressions the 1st hydrostatic support
The 4 expression conical surfaces
5 expression slide rails
5a, 5b, 5c, 5d, 5e represent encirclement portion
6 expression turning axlees
7a, 7b, 7c represent the pressure depression
8 expression pistons
9 expressions the 2nd hydrostatic support
13 expression spaces
14 expression pivots
15 expression cylinder barrels
21,22 expression flow routes
40a, 40b, 40c represent nozzle
42a, 42b, 42c represent fluid passage
50 expression sliding valve components
Claims (2)
1, rotary fluid energy conversion device is characterised in that: its structure comprises: internal surface is the casing and the torque ring of conical surface, this torque ring is by chimeric in the conical surface part of spaced the 1st hydrostatic support of circumferencial direction and said machine casing, and its inside is the plane that adapts with above-mentioned the 1st hydrostatic support; Several pistons in the internal arrangement of this torque ring, the end face of their fronts is closely contacted respectively with each inner plane of above-mentioned torque ring by the 2nd hydrostatic support; The cylinder that keeps the side of each piston head to slide, and supporting cylinder and the pivot that enables to rotate, pivot assemble to such an extent that depart from the axle center of said machine casing; Follow the relative rotation of said machine casing and torque ring, the space of the volume that between above-mentioned piston and said cylinder, forms increase and decrease, and, form the fluid flow route that is communicated with respectively in space and the ever-reduced space of volume that volume constantly increases; Fluid in above-mentioned each space is injected the fluid passage of the 1st and the 2nd hydrostatic support.So, rely on the static pressure of the fluid that injects last the 1st hydrostatic support and the static pressure of the fluid that injects above-mentioned the 2nd hydrostatic support, just can on above-mentioned torque ring, produce couple around running shaft, and, make above-mentioned each the 1st hydrostatic support, make and have a pair of pressure depression at least in the axle direction adjacency.By the throttling nozzle fluid of respective voids is diverted in above-mentioned each pressure depression.
2, rotary fluid energy conversion device is characterised in that: its structure comprises: internal surface is the casing and the torque ring of conical surface, this torque ring is by chimeric in the conical surface part of spaced the 1st hydrostatic support of circumferencial direction and said machine casing, and its inside is the plane that adapts with the 1st hydrostatic support; Several pistons in the internal arrangement of this torque ring,, the end face of their fronts is closely contacted respectively with each inner plane of above-mentioned torque ring by the 2nd hydrostatic support; The cylinder that keeps the side of each piston head to slide.And supporting cylinder and the pivot that enables to rotate, pivot assembles to such an extent that depart from the axle center of said machine casing; Follow the relative rotation of casing and torque ring, the space of the volume that forms between above-mentioned piston and cylinder increase and decrease, and, form the fluid flow route that is communicated with respectively in space and the ever-reduced space of volume that volume constantly increases; Fluid in above-mentioned each space is injected the fluid passage of the 1st and the 2nd hydrostatic support, so, rely on hydrostatic pressure that injects above-mentioned the 1st hydrostatic support and the static pressure that injects the fluid of above-mentioned the 2nd hydrostatic support, just can on above-mentioned torque ring, produce couple around running shaft, and, except being made, above-mentioned each the 1st hydrostatic support has several pressure depressions of axle direction adjacency, also utilize the effect of above-mentioned piston and torque ring in axial relative displacement, be provided with the sliding sleeve that to supply with fluid selectively to above-mentioned each pressure depression, so that the center of the pressure center of above-mentioned the 1st hydrostatic support and above-mentioned piston reduced in axial departing from as far as possible.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 85107656 CN1006999B (en) | 1985-10-18 | 1985-10-18 | Rotary fluid energy converter |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 85107656 CN1006999B (en) | 1985-10-18 | 1985-10-18 | Rotary fluid energy converter |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN85107656A true CN85107656A (en) | 1987-04-22 |
| CN1006999B CN1006999B (en) | 1990-02-28 |
Family
ID=4795713
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 85107656 Expired CN1006999B (en) | 1985-10-18 | 1985-10-18 | Rotary fluid energy converter |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN1006999B (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104040168A (en) * | 2012-01-11 | 2014-09-10 | 理查德·奈菲尔德 | Fluid flow energy converter |
| CN107002643A (en) * | 2014-12-10 | 2017-08-01 | 天才韦洛有限公司 | Fluid motor and fluid pump |
-
1985
- 1985-10-18 CN CN 85107656 patent/CN1006999B/en not_active Expired
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104040168A (en) * | 2012-01-11 | 2014-09-10 | 理查德·奈菲尔德 | Fluid flow energy converter |
| CN104040168B (en) * | 2012-01-11 | 2017-09-08 | 理查德·奈菲尔德 | Fluid stream kinetic energy convertor |
| CN107002643A (en) * | 2014-12-10 | 2017-08-01 | 天才韦洛有限公司 | Fluid motor and fluid pump |
Also Published As
| Publication number | Publication date |
|---|---|
| CN1006999B (en) | 1990-02-28 |
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