CN1806125A

CN1806125A - Fluid pump and motor

Info

Publication number: CN1806125A
Application number: CNA2004800165827A
Authority: CN
Inventors: 玄景烈
Original assignee: Individual
Current assignee: Individual
Priority date: 2003-06-13
Filing date: 2004-06-11
Publication date: 2006-07-19
Also published as: KR20040107541A

Abstract

A fluid pump of the present invention comprises a rotating chamber; a rotor which rotates about a rotating axis within the rotating chamber and includes a hub and a vane protruding radially outward from the hub; and a pair of blocking walls which cooperate with the vane and linearly move upon rotation of the rotor. A suction port for suction of a fluid and a discharge port for discharge of the fluid are provided at both positions adjacent to the pair of the blocking walls which are interposed between the ports.

Description

Oil hydraulic pump and fluid power motor

Technical field

The present invention relates to a kind of oil hydraulic pump and fluid power motor, particularly a kind of rotary type hydraulic pump and fluid power motor.

Background technique

Oil hydraulic pump is by the use driver element axle to be rotated, thus the device of suction and discharge fluid.Fluid power motor is to receive the fluid of discharging from pump, and makes the device of axle rotation.Oil hydraulic pump and fluid power motor are basic identical in configuration aspects.

Oil hydraulic pump of the prior art can be divided into the wing pump with slide member, the gear pump with two engaging gears, volute pump or the like.In these pumps, what often use is wing pump, and this is because its structure is simple relatively.Yet wing pump of the prior art should be configured to make its blade to pass in and out from rotor.In addition, wing pump has following structure problem.That is, may produce vibration in the wing pump, this is eccentric because of its running shaft, and because the load that is applied on the running shaft is non-equilibrium, so bearing may damage easily.In addition, because wing pump is not to discharge fluid continuously, therefore may produce pulsation (pulsation).

Disclosed a kind of structure pump different among the Korean Patent No.315954 with the rotary pump of prior art.This pump comprises: the seal container with suction pipe and discharge tube; Be installed in the transmission device that produces driving force in the described seal container; Limit the inner space, and comprise the drum assembly (cylinder assembly) of a plurality of suctions that are communicated with the inner space and discharge route; Connect with the rotor of transmission device, and the running shaft that penetrates from the center of drum assembly; Connect the inner space is divided into the dividing plate in first and second spaces with the running shaft in the drum assembly; Blade, it passes drum assembly and installs, and is flexibly supported, thereby it is contacted with the both sides of dividing plate all the time, and can move first and second spaces are converted to suction and discharge areas respectively; And opening/closing, when opening and closing the discharge route of drum assembly, discharge the compressed fluid in the constricted zone in first and second spaces.Yet, this pump that discloses among the Korean Patent No.315954 has following problem, promptly owing to become compression volume in the fixed single space of a lateral confinement of dividing plate, the amount of therefore discharging fluid is restricted, and because the width of constricted zone can change in time, and therefore the amount of discharging fluid also can change in time, therefore might produce pulsation.In addition, owing to must be provided for discharging the opening/closing (expulsion valve) of fluid, therefore be difficult to described pump as motor.

Summary of the invention

An object of the present invention is to provide a kind of rotary type hydraulic pump that is constructed to comprise blade and non-eccentricity.Another object of the present invention provides a kind of rotary type hydraulic pump with the simple vane that does not need to move into and shift out rotor.Another purpose of the present invention provides a kind of rotary type hydraulic pump that can increase discharge capacity.A further object of the present invention provides a kind of rotary type hydraulic pump that can reduce to pulse.Another purpose of the present invention provides a kind of rotary type hydraulic pump that can be used as motor.

According to an aspect of the present invention, provide a kind of oil hydraulic pump, can comprise at this: the rotating room, it is by the first and second relative wall surfaces and be used for interconnective the 3rd cylindrical wall of described first and second wall surfaces surface institute is limited; Rotor, it is around the spin axis rotation of passing the described first and second wall surface centers in the described rotating room, and comprise wheel hub and blade with outer circumferential face, described blade is outstanding and have an outside longitudinal end that closely contacts slidably with described the 3rd wall surface of described rotating room by the described outer circumferential face radially outward of described wheel hub; And a pair of retaining wall, itself and described blade collaborative work, and rotation linear motion according to described rotor, each described a pair of retaining wall has the opposite edges that face with each other by this way, the described opposite edges that are described retaining wall closely contact slidably with two side surfaces, and described retaining wall other edges adjacent with described opposite edges closely contact slidably with the described outer circumferential face of the described wheel hub of described rotor.Described blade further comprises and the described first wall surface of described the rotating room closely front end of contact, the rear end that closely contacts slidably with described second wall surface of described rotating room and the inclined-plane that is connected described front end and described rear end slidably.Be provided with the exhaust port that is used to suck the suction port of fluid and is used to discharge fluid in the position adjacent to described a pair of retaining wall, described retaining wall is inserted between described suction port and the exhaust port.

Described a pair of retaining wall can form as one each other.

Described the 3rd wall surface of described rotating room can be provided with suction tank and drain tank, described suction tank is adjacent with described a pair of retaining wall and be connected to described suction port, being connected to each other by each space that described blade is separated, described drain tank is adjacent with described a pair of retaining wall and be connected to described exhaust port, being connected to each other by each space that described blade is separated.

The described front-end and back-end of described blade can be formed with the described first and second wall surface faces of described rotating room and contact, and the width of the described longitudinal end of the described front-end and back-end of each described blade is formed greater than the ultimate range between corresponding suction tank and the drain tank.

Described oil hydraulic pump can further comprise first and second pressing plates, it defines described first and second wall surfaces of described rotating room, and described pressing plate closely contacts with the described front-end and back-end of described blade slidably along described spin axis linear motion and by external force.

Described pressing plate can be pushed to described rotating room by on high-tension side described fluid.

Described pressing plate can be pushed to described rotating room by elastic member.

Described oil hydraulic pump can further comprise regulator, be used to regulate discharge from described exhaust port and provide to the pressure of the fluid of load side.

Preferably, the fluid of discharging from described exhaust port flows to the return flow line that is communicated with low voltage side by first and second branched bottoms respectively, and the discharge route that is communicated with load side; And described regulator comprises the discharge capacity regulon, and described discharge capacity regulon has according to the hydrodynamic pressure in described discharge route motion with the moving element that opens and closes described first passage and be arranged on one-way valve in the described second channel.

Described regulator can further comprise elastic member, and the side that is used for being applied at the fluid with described discharge route the pressure of described moving element promotes described moving element in the opposite direction.

Preferably, be provided with two front ends, two rear ends and two pairs of retaining walls, and suction and drain tank be adjacent to described retaining wall setting, and separate by described two pairs of retaining walls.

Preferably, the direction of flow of discharging by described two exhaust ports that are positioned at described drain tank is connected to first and second passages of the return flow line that is communicated with low voltage side, and flow to third and fourth passage that is connected to the discharge route that is communicated with load side, and described regulator comprises the discharge capacity regulon, and described discharge capacity regulon has according to the hydrodynamic pressure in described discharge route motion to open and close described first or the moving element of second channel and be arranged on first and second one-way valves in described third and fourth passage respectively.

Described regulator can further comprise elastic member, is used for promoting described moving element in the side that described moving element is exerted pressure with the described fluid of described discharge route in the opposite direction.

Described regulator can further comprise the accumulation part.

Described accumulation part can comprise the moving element that moves by the pressure that receives the described fluid in the described discharge route, and is promoting the elastic member of described moving element in the opposite direction with the hydrodynamic pressure side that is applied to described moving element.

Described a pair of retaining wall can have and the contacted contact component of the both side surface of described blade, and in the described a pair of retaining wall each is provided with and is used to hold the receiving groove of described contact component and is used to make described receiving groove and discharges the through hole that side is communicated with.

According to another aspect of the present invention, provide a kind of fluid power motor, having comprised at this: the rotating room, it is by the first and second relative wall surfaces and be used for interconnective the 3rd cylindrical wall of described first and second wall surfaces surface institute is limited; Rotor, it is around the spin axis rotation of passing the described first and second wall surface centers in the described rotating room, and comprise wheel hub and blade with outer circumferential face, described blade is outstanding and have an outside longitudinal end that closely contacts slidably with described the 3rd wall surface of described rotating room by the described outer circumferential face radially outward of described wheel hub; And a pair of retaining wall, itself and described blade collaborative work, and rotation linear motion according to described rotor, each described retaining wall has the opposite edges that face with each other by this way, the described opposite edges that are described retaining wall closely contact slidably with two side surfaces, and described retaining wall other edges adjacent with described opposite edges closely contact slidably with the described outer circumferential face of the described wheel hub of described rotor.Described blade further comprises and the described first wall surface of described the rotating room closely front end of contact, the rear end that closely contacts slidably with described second wall surface of described rotating room and the inclined-plane that is connected described front end and described rear end slidably.Be provided with inlet that is used for incoming fluid and the outlet that is used for effluent fluid in the position adjacent to described a pair of retaining wall, described retaining wall is inserted between described inlet and the described outlet.

Described a pair of retaining wall can form as one each other.

Described the 3rd wall surface of described rotating room can be provided with and flow into groove and spout, described inflow groove is adjacent with described a pair of retaining wall and be connected to described inlet, being connected to each other by two spaces that described blade is separated, described spout is adjacent with described a pair of retaining wall and be connected to described outlet, being connected to each other by two spaces that described blade is separated.

The described front-end and back-end of described blade can be formed with the described first and second wall surface faces of described rotating room and contact, and the width of the described longitudinal end of the front-end and back-end of each described blade is formed greater than the ultimate range between corresponding suction tank and the drain tank.

Described fluid power motor can further comprise first and second pressing plates, it has formed described first and second wall surfaces of described rotating room, described pressing plate is along described spin axis linear motion, and closely contacts with the described front-end and back-end of described blade by external force.

Brief description of drawings

Fig. 1 is the stereogram of oil hydraulic pump according to the first embodiment of the present invention, wherein demonstrates the inside of pump main body by a part of removing pump case;

Fig. 2 is the side cutaway view of the main body of Fig. 2;

Fig. 3 is schematically illustrated in the oil hydraulic pump shown in Fig. 1 to discharge the amount of fluid is that the internal cross section figure of main body and regulator in the drawings, excises perpendicular to the shell of running shaft to main body under 100% the state;

Fig. 4 is the sectional drawing of the main body that A-A ' line obtains in Fig. 3;

Fig. 5 is the stereogram of the linear motion part (object) of the main body shown in Fig. 1;

Fig. 6 is the stereogram of the pressing plate of the main body shown in Fig. 1;

Fig. 7 is the stereogram of the opening/closing of the regulator shown in Fig. 3;

Fig. 8 (a) is the view that the rotor of the main body of Fig. 1 launches to (d), also shows the rotor and first and second retaining walls (blocking wall) in these figure;

Fig. 9 is schematically illustrated in the oil hydraulic pump shown in Fig. 1 to discharge the amount of fluid is that the internal cross section figure of main body and regulator in the drawings, excises perpendicular to the shell of running shaft to main body under 50% the state;

Figure 10 is schematically illustrated in the oil hydraulic pump shown in Fig. 1 to discharge the amount of fluid is that the sectional drawing of the inside of main body and regulator in the drawings, excises perpendicular to the shell of running shaft to main body under 0% the state;

Figure 11 is the stereogram of the oil hydraulic pump of second embodiment according to the present invention, wherein demonstrates the inside of pump main body by a part of removing pump case;

Figure 12 is schematically illustrated in the oil hydraulic pump shown in Figure 11 to discharge the amount of fluid is that the sectional drawing of the inside of main body and regulator in the drawings, excises perpendicular to the shell of running shaft to main body under 100% the state;

Figure 13 (a) is the view of rotor of expansion of the main body of Fig. 1 to (d), also shows the rotor and first and second retaining walls in these figure;

Figure 14 is schematically illustrated in the oil hydraulic pump shown in Figure 11 to discharge the amount of fluid is that the sectional drawing of the inside of main body and regulator in the drawings, excises perpendicular to the shell of running shaft to main body under 0% the state;

Figure 15 is the stereogram of main body of the oil hydraulic pump of third embodiment according to the present invention;

Figure 16 is the stereogram of the casing of the main body that C-C ' line obtains in Figure 15;

Figure 17 is the exploded perspective view of the linear motion part shown in Figure 16, and wherein, the core of linear motion part is removed, thereby can see the discharge side.

Preferred implementation of the present invention

Describe the preferred embodiments of the invention in detail hereinafter with reference to accompanying drawing.

Fig. 1 to Figure 10 is and the relevant view of first embodiment of the present invention.Referring to figs. 1 through Fig. 4, fluid pump 10 comprises main body 19 and regulator 90.Main body 19 comprises casing 20, rotor 30, running shaft 40, the first and second

linear motion parts

50 and 60, first and second pressing plates 70 and 80.Spin axis 100 is the lines that extend along running shaft 40.Casing 20 comprises cylindrical body part 21, and first and second alar parts 28 and 29 that are arranged on body portion 21 both sides.Body portion 21 comprises first and

second end walls

22 and 24, and the sidewall 26 that connects two end walls 22 and 24.First and

second end walls

22 and 24 form circular plate, and toward each other with vertical with spin axis 100.

First and second

pressing plates

70 and 80 inner spaces with body portion 21 be divided into first and second

pressing chambers

201 and 202 and rotating room's 23, the first and second

pressing plates

70 and 80 be mounted in order to cut apart the inner space and it is vertical with spin axis 100.First pressing chamber 201 is the space that is limited between first end wall 22 and first pressing plate 70, and second pressing chamber 202 is for being limited to the space between second end wall 24 and second pressing plate 80.Rotating room 23 is for being limited to the space between first and second pressing plates 70 and 80.Rotating room 23 is limited by first and second relative the 231 and 232 and the 3rd cylindrical wall surfaces, circular wall surface 233, and the 3rd cylindrical wall surface 233 connects first and second wall surfaces 231 and 232.First and

second wall surfaces

231 and 232 become the surface of facing first and second

pressing plates

70 and 80 respectively, and the part of the 3rd wall surface 233 on the internal surface of the sidewall 26 that becomes the body portion 21 that is limited to casing 20 between first and second pressing plates 70 and 80.The front end 341 of the blade 34 of the rotor 30 that will be explained below closely contacts with first wall surface 231 by this way with 345, can slide when to be it with the first wall surface contact, and two rear ends 343 of blade 34 closely contact with second wall surface 232 by this way with 347, can slide when promptly it contacts with second wall surface.The radial tip of blade 34 (tip) closely contacts slidably with the 3rd wall surface 233.

Running shaft 40 extends through two end walls 22 of body portion 21 and 24 center along spin axis 100.Running shaft 40 is rotatably supported by the

bearing

42 and 44 that is installed in two

end walls

22 and 24 centers.Running shaft 40 extends beyond first end wall 22 along spin axis 100, and is connected with the driver element (not shown).

With reference to Fig. 1 and Fig. 3, first suction tank 261, first drain tank 262, second suction tank 263 and second drain tank 264 are arranged on the 3rd wall surface 233 of rotating room 23 in succession.Each groove 261,262,263 and 264 and spin axis 100 extend side by side.First and

second suction tanks

261 and 263 are arranged with respect to spin axis 100 with being mutually symmetrical.First and

second drain tanks

262 and 264 are arranged with respect to spin axis 100 with being mutually symmetrical.

First suction tank

261 and 264 settings adjacent one another are of second drain tank, and

first drain tank

262 and 263 settings adjacent one another are of second suction tank.Be provided with first movable part 50 between first suction tank 261 and second drain tank 264.In addition, be provided with second movable part 60 between first drain tank 262 and second suction tank 263.First and

second suction tanks

261 and 263 special position (for example center) are respectively arranged with first and second suction ports 2611 and 2631.First and second suction ports 2611 are connected with 17 with first and second suction pipes 15 respectively with 2631.First and

second drain tanks

262 and 264 special position (for example center) are respectively arranged with first and second exhaust ports 2621 and 2641.First and second exhaust ports 2621 are connected with 18 with first and second discharge tubes 16 respectively with 2641.Yet the present invention is not limited only to this.That is, the position of first and

second suction ports

2611 and 2631 and first and

second exhaust ports

2621 and 2641 can change.

Referring to figs. 1 through Fig. 4, first alar part 28 is formed from two

end walls

22 and 24 and is parallel to spin axis 100 extensions towards opposite direction.In addition, first alar part 28 from sidewall 26 inwardly or stretch out is formed in radial direction.Therefore, first alar part 28 has along the upright narrow rectangular cross-section of the radial direction of spin axis 100, but is not formed in the space that is formed with body 21.First alar part 28 is provided with first and leads the way (guide passage) 281, the first movable parts 50 along first 281 linear motions of leading the way.First lead the way 281 the sectional shape is identical with the sectional shape of first movable part 50.First 281 two

end walls

22 and 24 from casing 20 of leading the way extend in the direction that is parallel to spin axis 100, and also at the sidewall that extends beyond casing 20 in the radial direction 26 of spin axis 100.

First suction tank

261 and 264 settings adjacent one another are of second drain tank, and first lead the way and 281 be inserted between the two and (see Fig. 3 and Fig. 4).Through hole 282 is respectively formed at vertical two ends of first alar part 28.First leads the way 281 by through hole 282 and external communications, and the first linear motion part 50 can be in first motion glossily in 281 of leading the way thus.Because second alar part 29 and first alar part 28 are provided with symmetrically with respect to spin axis 100, therefore omit its detailed description at this.The second linear motion part 60 is arranged on second in second alar part 29 and leads the way in 291, and

first drain tank

262 and 263 settings adjacent one another are of second suction tank, and second leads the way 282 is inserted between the two.

Referring again to Fig. 1 to Fig. 4, rotor 30 is arranged in the rotating room 23 of casing 20 inside, and comprises tubular wheel hub (hub) 32, and wheel hub 32 engages with running shaft 40 with at the blade of giving prominence to from wheel hub 32 in the radial direction 34.The opposite end of wheel hub 32 respectively with rotating room 23 in first and second wall surfaces 231 closely contact slidably with 232.Running shaft 40 passes the center of the opposite end of wheel hub 32.The radius of wheel hub 32 is designed to this size, and promptly first and second retaining walls 64 of first and second retaining walls 54 of its outer circumferential face 321 and the first

linear motion part

50 and 56 the edge 541 and the 651 and second

linear motion part

60 and 66 edge 641 closely contact slidably with 661.Flow in the space that fluid passes through to limit between the 3rd wall surface 233 of the outer circumferential face 321 of wheel hub 32 and rotating room 23.

Still referring to figs. 1 through Fig. 4, blade 34 is from the outer circumferential face 321 of wheel hub 32 shape with the outstanding wall of radial direction, and around the outer circumferential face 321 of wheel hub 32, thereby the surface that makes its both sides is respectively in the face of first and

second wall surfaces

231 and 232 of rotating room 23.In this article, be called as first surface 340 in the face of of the first wall surface 231 of rotating room 23 in the

side surface

340 and 349, and be called as second surface 349 in the face of another of second wall surface 232 of rotating room 23 in above-mentioned two surfaces.

Referring to figs. 1 through Fig. 4 and the Fig. 8 (a) that wherein shows the rotor 30 of expansion (unroll), blade 34 comprises two

front ends

341 and 345, two

rear ends

343 and 347 and four inclined-planes 342,344,246 and 348, wherein,

front end

341 and 345 is mutually symmetrical with respect to spin axis 100, and flat surface with predetermined width vertical (angular breadth) with spin axis, thereby making it carry out the surface slidably with the first wall surface 231 of rotating room 23 contacts,

rear end

343 and 347 is mutually symmetrical with respect to spin axis 100, and flat surface with predetermined width vertical (angular breadth) with spin axis, thereby make it carry out the surface slidably and contact inclined-plane 342 with second wall surface 232 of rotating room 23,344,246 tilt and are connected front-end and back-end 341 with respect to spin axis 100 with 348,343,345 and 347.Blade 34 is constructed by this way, and promptly front end 341, inclined-plane 342, rear end 343, inclined-plane 344, front end 345, inclined-plane 346, rear end 347 and inclined-plane 348 are connected on the circumferencial direction of spin axis 100 smoothly successively.The outward radial tip of blade 34 is closely contacting slidably with the 3rd surface 233 of rotating room 23 in the radial direction with respect to spin axis 100.Two retaining walls 54 of the first linear motion part 50 and two opposed edges 542 and 562 of 56, and first and second surfaces 340 of two retaining walls 64 of the second linear motion part 60 and two opposed edges 642 of 66 and 662 (being described in the following) and blade 34 closely contact slidably with 349.The thickness of blade 34 is confirmed as when rotor 30 rotation, and two retaining walls 64 of two retaining walls 54 that make the linear motion part 50 of winning and 56 two opposed edges 542 and the 562 and second linear motion part 60 and two opposed edges 642 of 66 closely contact with 349 with first and second surfaces 340 all the time slidably with 662.Preferably, the thickness of blade 34 is determined to be on the first and second

linear motion parts

50 and 60 directions of extending, and the distance between first and

second surfaces

340 and 349 remains unchanged basically.

Because this structure of blade 34, the space that limits between the 3rd wall surface 233 of the outer circumferential face 321 of the wheel hub 32 of rotor 30 and rotating room 23 is divided into the first and the

3rd space

11 and 13 that the first surface 340 by the first wall surface 231 of rotating room 23 and blade 34 forms, and the second and the

4th space

12 and 14 that is formed by the second surface 349 of second wall surface 232 of rotating room 23 and blade 34.

Front end

341 and 345 and the width (angular breadth) of the radial tip of

rear end

343 and 347 be formed greater than the maximum angular distance the maximum angular distance between first suction tank 261 and second drain tank 264 (i.e. angular distance from the distal-most end of first suction tank to the distal-most end of second drain tank) and second suction tank 263 and first drain tank 262.

Referring to figs. 1 through Fig. 5, the first linear motion part 50 is the shape of the straight thin plate of elongated, and comprise base portion 52 and first and second

retaining walls

54 and 56, base portion 52 is positioned at the outer relatively in the radial direction position of spin axis 100, first and

second retaining walls

54 and 56 inside vertically upright from base portion 52 in the radial direction at spin axis 100.First and second

retaining walls

54 and 56 define a pair of retaining wall.First and second retaining walls 54 are identical with the height of the blade 34 of rotor 30 with 56 height.First and

second retaining walls

54 and 56 inward flange 541 and 561 be the diminishing gradually in the radial direction of spin axis 100, and closely contact slidably with the outer circumferential face 321 of the wheel hub 32 of rotor 30.Therefore, can reduce the wheel hub 32 of rotor 30 and the frictional force between first and second retaining walls 54 and 56.First and second

retaining walls

54 and 56 opposed edges 542 and 562 also diminish gradually, and closely contact slidably with 349 with first and second surfaces 340 of the blade 34 of rotor 30.The inward flange 521 of base portion 52 between first and second

retaining walls

54 and 56 closely contacts slidably with the outward radial tip of blade 34.The first linear motion part 50 is set at first of casing 20 and leads the way in 281, and when rotor 30 rotations by blade 34 along first 281 linear motions of leading the way.The second linear motion part 60 is constructed to and the first linear motion part, 50 symmetries, and is arranged on second of second alar part 29 and leads the way in 291.Therefore, omitted second linear motion detailed description partly at this.

Shown in Fig. 8 (a) (wherein blade is unfolded), when the first and second

linear motion parts

50 and 60 lay respectively in the inclined-

plane

342 and 346 of blade 34 (perhaps when described part be arranged in other inclined-

plane

344 and 348 the time), first retaining wall 54 of the first linear motion part 50 is divided into first and

second subspaces

111 and 112 with first space 11, and intercepts two sub spaces 111 and 112.In addition, second retaining wall 56 of the first linear motion part 50 is divided into first and

second subspaces

121 and 122 with second space 12, and intercepts two sub spaces 121 and 122.Similarly, first retaining wall 64 of the second linear motion part 60 is divided into first and

second subspaces

131 and 132 with the 3rd space 13, and intercepts two sub spaces 131 and 132.In addition, second retaining wall 66 of the second linear motion part 60 is divided into first and

second subspaces

141 and 142 with second space 14, and intercepts two sub spaces 141 and 142.Otherwise, as Fig. 8 (a) to shown in 8 (b), when the first and second

linear motion parts

50 and 60 lay respectively at the front end 341 of

blade

34 and 345 the time, have only the second and the

4th space

12 and 14 to be in the state that is divided into two sub spaces respectively by second

retaining wall

56 and 66 of the first and second linear motion parts 50 and 60.Though it is also not shown among the figure, but those skilled in the art understand easily, when the first and second

linear motion parts

50 and 60 lay respectively at the rear end 343 of

blade

34 and 347 the time, have only the first and the

3rd space

11 and 13 to be divided into two sub spaces by second

retaining wall

54 and 64 of the first and second

linear motion parts

50 and 60 respectively.

With reference to the shape of Fig. 1,2,4 and 7, the first pressing plates, 70 rounded plates, and comprise the circular perforations 71 that is formed on its center, first and second grooves 72 that extend to its center from its outer periphery and 74 and

contiguous groove

72 and 74 through

holes

76 and 78 that form.The outer periphery 701 of first pressing plate 70 closely contacts slidably with the sidewall 26 of casing 20.Running shaft 40 passes center hole 71.First and

second grooves

72 and 74 are formed with respect to center hole 71 and are mutually symmetrical.In two

grooves

72 and 74 each has and first retaining wall 54 of the first and second

linear motion parts

50 and 60 or 64 the identical shape of sectional shape.The first and second linear motion parts 50 and two

first retaining walls

54 and 64 of 60 are slidably mounted in respectively in two grooves 72 and 74.Two through

holes

76 and 78 roughly be mutually symmetrical, and be arranged on discharge side of rotating room with respect to spin axis 100.The high-pressure liquid that rotating room 23 discharges side provides to first pressing chamber 201 by two through holes 76 and 78.Because second pressing plate 80 has the shape identical with first pressing plate 70, therefore omits its detailed description at this.

Two surfaces of facing mutually of first and second pressing plates 70 become first and second wall surfaces 231 and 232 of rotating room 23.High-pressure liquid in first and second

pressing chambers

201 and 202 applies power in opposite direction rotor 30 is exerted pressure on these two wall surfaces.Apply power come rotor pressurization on first and second

pressing plates

70 and 80 though described high-pressure liquid in the present embodiment, the present invention is not limited to this.It will be appreciated by those skilled in the art that can by elastic member for example coil compression springs rotor is pressurizeed.

With reference to Fig. 3, regulator 90 comprises discharge capacity regulon 91 and the compression unit 96 that is arranged in the frame (block) 900.Discharge capacity regulon 91 comprises moving element 92, elastic member 93, first and second one-way valves 94 and 95.Moving element 92 and elastic member 93 are contained in first and receive in the space 901.First receives space 901 is formed cylindricality, and comprises rounded bottom 902 and round tip 903, and the sidewall 904 that connects bottom and top 902 and 903.Link to each other with discharge route 150 and the pressure transmission of the exhaust fluid first voltage supply passage 151 (will be described later) to the moving element 92 that links to each other with load side is connected with bottom 902, the outrigger shaft 924 (will be described later) of moving element 92 is inserted in the first voltage supply passage 151.Be connected to first through hole 9033,903 formation of the 7th path 10 7 (will be described later) on the top.Be connected to first and first and second inlets 9041 and 9042 of third channel 101 and 103 (will be described later) centre that is formed on sidewall 904.First and second inlets 9041 and 9042 relatively are provided with near bottom 902 and top 903 respectively.Sidewall 904 is being provided with first and second outlets 9043 and 9044 that are connected to the 5th and the 6th path 10 5 and 106 (will be described later) respectively with first and second inlets, 9041 and 9042 relative positions.Sidewall 904 also is provided with second through hole 9045 that is connected to the 8th path 10 8 (will be described later) in the position of adjacent top end 903.

The discharge tube 16 that extends from the main body 19 of oil hydraulic pump 10 is bifurcated and enters first and second path 10s 1 and 102.First passage 101 receives space 901 by first inlet 9041 and first and is communicated with, and second channel 102 is connected with discharge route 150.First one-way valve 94 is arranged on the second channel 102, in case fluid stopping body reverse flow.Second discharge tube 18 that extends from main body 19 is bifurcated and enters third and fourth path 10 3 and 104.Third channel 103 receives space 901 by second inlet 9042 and first and is communicated with, and four-way 104 is connected with discharge route 150.Second one-way valve 95 is arranged on the four-way 104, in case fluid stopping body reverse flow.Though first and second outlets, 9043 the 5th and the 6th path 10s 5 and 106 that link to each other with 9044 in also not shown and the first reception space 901, they are connected to the return flow line 160 that is communicated with low voltage side (for example holding vessel).The 8th path 10 8 connects second through hole 9045 and the 6th path 10 6.The 7th path 10 7 connects first through hole 9033 and is arranged on the third through-hole 9631 that second of compression unit 96 receives the top 963 in space 961.Thus, first and second receive spaces 901 and always link to each other with low voltage side with 961 top.

With reference to Fig. 3 and Fig. 7, moving element 92 comprises opening/closing part 921, attachment post 922, enclosure portion 923 and the outrigger shaft 924 that sets gradually from the top down.Opening/closing part 921 is formed cylindricality, and its radius is determined to be and outer circumferential face 9211 can be received on the sidewall 904 in space 901 first slide.The height of opening/closing part 921 is confirmed as making outer circumferential face 9211 will be arranged on first first and second inlets, 9041 and 9042 and first and second outlets, 9043 and 9044 sealings that receive on the sidewall 904 in space 901.Attachment post 922 is formed cylindricality, and its radius is less than the radius of opening/closing part 921, thereby makes outer circumferential face 9221 not contact with first sidewall 904 that receives space 901.In addition, the height of attachment post 922 is confirmed as making when moving element 922 moves to its extreme higher position, is arranged on first and receives first and second inlets 9041 and 9042 and first and second on the sidewall 904 in space 901 and export 9043 and 9044 intervals that can be positioned at attachment post.Enclosure portion 923 has the shape of thin dish, and its radius is confirmed as making outer circumferential face 9231 to slide on the sidewall 904 in the first reception space 901.Outrigger shaft 924 has thin circular pin shape, and its radius is confirmed as making and it can be inserted securely in the first voltage supply passage 151 that links to each other with first bottom 902 that receives space 901, and along 151 slips of the first voltage supply passage.Hydraulic pressure in the discharge route 150 is applied to the far-end of outrigger shaft 924.Be in application under the effect of hydraulic pressure of outrigger shaft 924 far-ends, moving element 92 moves upward.Moving element 92 can receive vertical motion in the space 901 first.Elastic member 93 is compression disc springs, and the upper end of the opening/closing part 921 of the top 903 in its two ends and the first reception space 901 and moving element 92 engages.The bottom 902 that elastic member 93 towards first receives space 901 promotes moving element 92.Moving element 92 is promoted downwards by elastic member 93, thus when the bottom that enclosure portion 923 and first receives space 901 contacts, the outer circumferential face 9211 of opening/closing part 921 will be arranged on first first and second inlets, 9041 and 9042 and first and second outlets, 9043 and 9044 sealings that receive on the sidewall 904 in space 901.

With reference to Fig. 3, compression unit 96 comprises moving element 97 and elastic member 98.Moving element 97 and elastic member 98 are contained in second and receive in the space 961.Second receives space 961 is formed cylindricality and comprises rounded bottom 962 and round tip 963, and the sidewall 964 that connects bottom 962 and top 963.Link to each other with discharge route 150 and the pressure transmission of the exhaust fluid second voltage supply passage 152 to moving element 97 is connected with bottom 962, the outrigger shaft 972 (will be described later) of moving element 97 is inserted in the second voltage supply passage 152.Be connected to third through-hole 9,631 963 formation of the 7th path 10 7 on the top.

Still with reference to Fig. 3, moving element 97 comprises piston 971 and the outrigger shaft 972 that sets gradually from the top down.Piston 971 is formed cylindricality, and its diameter is set so that outer circumferential face 9711 can slide on the sidewall 964 in the second reception space 961.Piston 971 can receive vertical motion in the space 961 second.Outrigger shaft 972 also is formed cylindricality, and is inserted securely in the second voltage supply passage 152 that links to each other with second bottom 962 that receives space 961 and along the second voltage supply passage 152 and slide.Hydraulic pressure in the discharge route 150 is applied to the far-end of outrigger shaft 972.Elastic member 98 is compression disc springs, and the upper end of the piston 971 of the top 963 in its two ends and the second reception space 961 and moving element 97 engages.The bottom 962 that elastic member 98 towards second receives space 961 promotes moving element 97.

Describe the work of oil hydraulic pump according to the first embodiment of the present invention in detail hereinafter with reference to Fig. 3, Fig. 8 (a) to (d), Fig. 8 and Figure 10.The work of main body 19 at first, is described with reference to Fig. 8 (a) to (d).Fig. 8 (a) to (d) shows the rotor 30 of expansion.In the drawings, rotor 30 is shown as solid line, and groove 261,262,263 and 264, suction port 2611 and 2631 and exhaust port 2621 and 2641 be shown as dotted line.If running shaft 40 drived unit (not shown) clockwise rotate as illustrated in fig. 1, then rotor 30 also turns clockwise.This rotation is corresponding to rotor 30 linear motion to the left of the expansion shown in Fig. 8 (a).In Fig. 8 (a), the first and second linear motion parts 50 and 60 lay respectively on two inclined-planes 342 and 346 of blade 34.With reference to Fig. 8 (a), the first and the 4th space 11 and 14 second subspace 112 and 142 communicate with each other by first suction tank 261, the second and the 3rd space 12 and 13 first subspace 121 and 131 communicate with each other by first drain tank 262, the second and the 3rd space 12 and 13 second subspace 122 and 132 communicate with each other by second suction tank 263, and first subspace 141 of the 4th and first space 14 and 11 and 111 communicates with each other by second drain tank 264.If rotor 30 rotates with this state, two sub spaces 112 that communicate with each other by first suction tank 261 and 142 and can increase so by two sub spaces 122 and 132 that second suction tank 263 communicates with each other.Thus, fluid is inhaled into by first and second suction ports 2611 and 2631.The fluid that sucks is introduced into each sub spaces 112,142,122 and 132 that is interconnected by first and second suction tanks 261 and 263.Simultaneously, two sub spaces 121 that communicate with each other by first drain tank 262 and 131 and can reduce by two sub spaces 141 and 111 that second drain tank 264 communicates with each other.Thus, the fluid in the subspace 121,131,141 and 111 is discharged to first and second exhaust ports 2621 and 2641 by first and second drain tanks 262 and 264.Fig. 8 (b) shows when rotor 30 is further rotated, and the first and second linear motion parts 50 and 60 arrive two front ends 341 of blades 34 and 345 state.

With reference to Fig. 8 (b), first and second suction tanks 261 and 263 lay respectively on the inclined-plane 342 and 346 of blade 34, and first and second drain tanks 262 and 264 lay respectively on two front ends 341 and 345.At this moment, second subspace 142 in first space 11 and the 4th space 14 communicates with each other by first suction tank 261, and second subspace 122 in the 3rd space 13 and second space 12 communicates with each other by second suction tank 263, first drain tank 262 is all linking to each other with first subspace 121 in second space 12 on the length, and second drain tank 264 is all linking to each other with first subspace 141 in the 4th space 14 on the length.If rotor 30 is rotation in this state further, then second subspace 142 and 122 increases.Thus, fluid is inhaled into by first and second suction ports 2611 and 2631.The fluid that sucks is introduced in the subspace 142 and 122 of two increases.Simultaneously, reduce with two sub spaces 121 and 141 that first and second drain tanks 262 link to each other with 264.Thus, the fluid in two sub spaces 121 and 141 is discharged by first and second exhaust ports 2621 and 2641.Fig. 8 (c) shows after rotor 30 is further rotated, and the first and second linear motion parts 50 and 60 arrive two front ends 341 of blades 34 and 345 state.

With reference to Fig. 8 (c), first suction tank 261 and second drain tank 264 are positioned on the front end 341, and second suction tank 263 and first drain tank 262 are positioned on the front end 345.At this moment, first suction tank 261 is all linking to each other with second subspace 142 in the 4th space 14 on the length, and first drain tank 262 is all linking to each other with first subspace 121 in second space 12 on the length, second suction tank 263 is all linking to each other with second subspace 122 in second space 12 on the length, and second drain tank 264 is all linking to each other with first subspace 141 in the 4th space 14 on the length.If further with this state rotation, then second subspace 142 and 122 increases rotor 30, and fluid is inhaled into by first and second suction ports 2611 and 2631 thus.The fluid that sucks is introduced in the subspace 142 and 122 of two increases.Simultaneously, subspace 121 and 141 reduces, and the fluid in two sub spaces 121 and 141 is discharged by first and second exhaust ports 2621 and 2641.Because first and second suction tanks 261 and 263 and first and second drain tanks 262 and 264 are positioned at front end 341 and 345 simultaneously, so suction tank 261 and 263 is not communicated with drain tank 262 and 264.Therefore, suction tank 261 and 263 always is communicated with drain tank 262 and 264.Therefore, do not need to be used to prevent the additional one-way valve (often being called " expulsion valve ") of fluid reflux.Fig. 8 (d) shows after rotor 30 is further rotated, and the first and second linear motion parts 50 and 60 arrive the front end 341 of blade 34 and the state of 345 end points respectively on angle direction.

With reference to Fig. 8 (d), first and second suction tanks 261 and 263 lay respectively on two front ends 341 and 345 of blade 34, and first and second drain tanks 262 and 264 lay respectively on the inclined-plane 344 and 348 of blade 34.At this moment, first suction tank 261 is all linking to each other with second subspace 142 in the 4th space 14 on the length, and second suction tank 263 is all linking to each other with second subspace 122 in second space 12 on the length.In addition, first subspace 121 in first space 11 and second space 12 communicates with each other by first drain tank 262, and first subspace 141 in the 3rd space 13 and the 4th space 14 communicates with each other by second drain tank 264.If rotor 30 is further with the rotation of this state, then subspace 142 and 122 increases, thereby and fluid be inhaled into by first and second suction ports 2611 and 2631.The fluid that sucks is introduced in the subspace 142 and 122 of two increases.Simultaneously, space 11 that communicates with each other by first drain tank 262 and subspace 121 and can reduce by space 13 and subspace 141 that second drain tank 264 communicates with each other, and the fluid in them is discharged by first and second exhaust ports 2621 and 2641 thus.When rotor 30 continued rotation, said process repeated by this way, and promptly fluid is constantly sucked by two suction ports 2611 and 2631, and discharges by two exhaust ports 2621 and 2641.At this moment, because two spaces of being separated by blade 34 are connected with each other by first and second suction tanks 261 and 263 and first and second drain tanks 262 and 264, therefore can suck and discharge the fluid of fixed amount basically all the time, thereby make minimum pulsation.In addition, therefore the setting because suction and exhaust port are mutually symmetrical basically can improve spin balancing.Noise and vibration have been reduced thus.

With reference to Fig. 1,2 and 4, first and second through

holes

76,78 and 86,88 high-pressure liquids with the waste side in the rotating room 23 by first and second

pressing plates

70 and 80 provide to first and second

pressing chambers

201 and 202 respectively.High-pressure liquid makes first and second pressing plates 70 closely contact with rotor 30 with 80 in addition, thereby prevents that fluid from spilling.

By the aforesaid operations of main body 19, the fluid of discharge is introduced regulator 90 by first and second discharge tubes 16 and 18.With reference to Fig. 3, the moving element 92 of the discharge capacity regulon 91 of regulator 90 is by the pushed down of elastic member 93 position extremely bottom.In this state, opening/closing part 921 sealings of first and second inlets, 9041 and 9042 and first and second outlets, 9043 and 9044 passive movement parts 92.Thus because the fluid of discharging from main body 19 by first and

second discharge tubes

16 and 18 through second and four-way 102 and 104 discharge by discharge route 150, the amount of therefore discharging fluid is 100%.In addition, the moving element 97 of compression unit 96 is in the upwards slight state that promotes of the hydrodynamic pressure that is discharged from the passage 150.

If the hydrodynamic pressure in the discharge route 150 increases with this state, then the moving element 92 of discharge capacity regulon 91 moves upward against elastic member 93 owing to hydrodynamic pressure, as shown in Figure 9.With reference to Fig. 9, the position of the opening/closing part 921 of the moving element 92 of discharge capacity regulon 91 allows first entrance and

exit

9041 and 9043 to open and second entrance and

exit

9042 and 9044 is closed.Therefore, because discharge by the return flow line 160 that is connected to low voltage side by the fluid that first discharge tube 16 is discharged from main body 19, and only being to discharge by discharge route 150 from the fluid that main body 19 is discharged by second discharge tube 18, is 50% so discharge the amount of fluid.At this moment, first one-way valve 94 can prevent that the high-pressure liquid in the discharge route 150 from refluxing.

If the hydrodynamic pressure in the discharge route 150 is greater than the state shown in Fig. 9, then the moving element 92 of discharge capacity regulon 91 further moves upward, as shown in figure 10.With reference to Figure 10, the position of the opening/closing part 921 of the moving element 92 of discharge capacity regulon 91 allows 9041 and 9042 and first and

second outlets

9043 and 9044 of first and second inlets to open.Therefore, because the fluid of being discharged by first and

second outlets

9043 and 9044 from main body 19 passes through return flow line 160 discharges, the amount of therefore discharging fluid is 0%.At this moment, first and second one-way valves 94 and 95 can prevent that the high-pressure liquid backflow in the discharge route 150 from entering first and

second discharge tubes

16 and 18.

If hydrodynamic pressure is less than the state shown in Fig. 9 or Figure 10, then the moving element 92 of elastic member 93 promotion discharge capacity regulons 91 moves, with the FLUID TRANSPORTATION that will discharge by first or

second discharge tube

16 or 18 to discharge route 150, thereby can increase the amount of discharging fluid.At this moment, the moving element 97 of compression unit 96 is promoted downwards by elastic member 98, and the FLUID TRANSPORTATION that will be retained in the second voltage supply passage 152 arrives in the discharge route 150.Therefore, the pressure that descends in the discharge route 150 rises to specified point again.

Figure 11 to 14 shows second embodiment of the present invention.With reference to Figure 11 and 12, fluid pump 10a comprises main body 19a and regulator 90a.Main body 19a comprises casing 20a, rotor 30a, running shaft 40a and linear motion part 50a.The direction that running shaft 40a extends is spin axis 100a.Casing 20a comprises cylindrical body part 21a and alar part 28a.Body portion 21a comprises first and second circular end wall 22a and the 24a, and the sidewall 26a that connects two end wall 22a and 24a.The 23a of cylindricality rotating room that wherein accommodates rotor 30a is arranged in the body portion 21a.The 23a of rotating room is limited by first and second relative circular walls surface 231a and 232a and the 3rd circular wall surface 233a, and the surperficial 233a of the 3rd circular wall connects first and second wall surface 231a and the 232a.The first and second wall surface 231a and 232a are the first and second end wall 231a of body portion 21a and the internal surface of 2323a, and the 3rd wall surface 233a is the internal surface of the sidewall 26a of body portion 21a.The front end 341a of the blade 34a that will be explained below closely contacts by this way with first wall surface 231a, can slide when to be it with the first wall surface contact, and the rear end 343a of blade 34 closely contacts by this way with the second wall surface 232a, can slide when promptly it contacts with second wall surface.Radial tip (will be described later) around the blade 34 of the spin axis 100a of blade 34a closely contacts slidably with the 3rd wall surface 233a.Running shaft 40a passes the center of two end wall 22a and the 24a of body portion 21a.Running shaft 40a is rotatably supported by the bearing 42a and the 44a that are installed in two end wall 22a and 24a center respectively.Running shaft 40a extends beyond the first end wall 22a along spin axis 100a, and rotatably is connected with the driver element (not shown).

With reference to Figure 11 and 12, on the suction tank 261a of straight-line extension to the first and second wall surface 231a and 232a on extension (vertically) direction of spin axis 100a and drain tank 262a are formed adjacent to each other the 3rd wall surface 233a at the 23a of rotating room.The first and second retaining wall 54a and the 56a of linear motion part 50a (will be described later) are arranged between suction tank and drain tank 261a and the 262a.Suction port 2611a and exhaust port 2621a are separately positioned on the center of suction tank and drain tank 261a and 262a.Suction pipe 15a and discharge tube 17a are connected to suction port 2611a and exhaust port 2621a respectively.Except having used the single alar part 28 in this second embodiment, the structure of the alar part of describing in the structure of alar part 28a and first embodiment 28 is identical.Therefore omit its detailed description at this.

Still with reference to Figure 11 and 12, rotor 30a is positioned at the 23a of rotating room of casing 20a, and comprises tubular wheel hub 32a, and wheel hub 32a engages with running shaft 40a with from the outstanding blade 34a of wheel hub 32a.The opposite end of wheel hub 32a respectively with the 23a of rotating room in the first and second wall surface 231a closely contact slidably with 232a.Blade 34a is the shape with the outstanding wall of the radial direction of spin axis 100a from the outer circumferential face 321a of wheel hub 32a, and, thereby make the surperficial 340a of blade both sides and first and second wall surface 231a and the 232a that 349a faces the 23a of rotating room respectively around the outer circumferential face of wheel hub 32a.At this, be called as first surface 340a in the face of of the first wall of the 23a of rotating room surface 231a among side surface 340a and the 349a, and be called as second surface 349a in the face of another of the second wall surface 232a of the 23a of rotating room in two surfaces.

With reference to Figure 11 and 12 and Figure 13 (a) of wherein showing the rotor 30a of expansion, blade 34a comprises flat front end 341a, flat rear end 343a and two inclined-plane 342a and 344a, wherein front end 341a has the predetermined width vertical with spin axis 100a (angular breadth), thereby it can carry out the surface with the first wall surface 231a of the 23a of rotating room and contact, rear end 343a has the predetermined width vertical with spin axis 100a (angular breadth), thereby it can carry out the surface with the second wall surface 232a of the 23a of rotating room and contacts, and inclined-plane 342a tilts with respect to spin axis 100a with 344a and is connected front-end and back-end 341a and 342a.Outward radial tip around the blade 34a of spin axis 100a closely contacts slidably with the 3rd wall surface 233a of the 23a of rotating room.Because this structure of blade 34a, the space that limits between the 3rd wall surface 233a of the outer circumferential face 321a of the wheel hub 32a of rotor 30a and the 23a of rotating room is divided into the first space 11a that the first surface 340a by the first wall surface 231a of the 23a of rotating room and blade 34a forms, and the second space 12a that is formed by the second surface 349a of the second wall surface 232a of the 23a of rotating room and blade 34a.Front end 341a and rear end 343a are set to that (diametrically) toward each other toto caelo with respect to spin axis 100a.The width of the radial tip of front end 341a and rear end 343a (angular breadth) is formed greater than the maximum angular distance between suction tank 261a and the drain tank 262a (i.e. angular distance from the distal-most end of suction tank to the distal-most end of drain tank) (seeing Figure 12 (c)).Two inclined-plane 342a and 344a tilt with respect to spin axis 100a, and connect front end 341a and rear end 343a.That is to say that blade 34a constructs by this way, promptly front end 341a, inclined-plane 342a, rear end 343a, inclined-plane 344a interconnect successively, and being arranged in a week on its outer circumferential face 321a around wheel hub 32a.

Because linear motion part 50a is structurally identical with the first linear motion part 50, therefore omit its detailed description at this.Shown in Figure 13 (a), when linear motion part 50a is positioned at the inclined-plane 342a of blade 34a (perhaps when described part is positioned at another inclined-plane 344a), the first retaining wall 54a is divided into first and second subspace 111a and the 112a with the first space 11a, and intercepts two sub spaces 111a and 112a.In addition, the second retaining wall 56a is divided into first and second subspace 121a and the 122a with the second space 12a, and intercepts two sub spaces 121a and 122a.On the contrary, shown in Figure 13 (b) to (d), when linear motion part 50a is positioned at the front end 341a of blade 34a, the first space 11a is not cut apart by the first retaining wall 54a but is remained single space, but the second space 12a still is in the state that is divided into two sub spaces 121a and 122a by the second retaining wall 56a.Though also not shown among the figure, one of ordinary skill in the art will readily recognize that when linear motion part 50a is positioned at the rear end 343a of blade 34a to have only the first space 11a to be divided into two sub spaces by the first retaining wall 54a.

With reference to Figure 12, regulator 90a comprises discharge capacity regulon 91a and the compression unit 96a that is arranged among the frame 900a.Discharge capacity regulon 91a comprises moving element 92a, elastic member 93a and one-way valve 94a.Moving element 92a and elastic member 93a are contained in first and receive in the 901a of space.The inlet 9041a that is connected to first passage 101a (will be described later) is formed on the centre of sidewall 904a.Sidewall 904a is provided with the outlet 9043a that is connected to third channel 105a (will be described later) in the position with respect to inlet 9041a.The discharge tube 16a bifurcated that extends from the main body 19a of oil hydraulic pump 10a enters first and second path 10 1a and the 102a.First passage 101a receives space 901a by the first inlet 9041a and first and is communicated with, and second channel 102a is connected with discharge route 150a.Second channel 102a is provided with one-way valve 94a, in case fluid stopping body reverse flow.Though the third channel 105a also not shown and the first outlet 9043a that receives space 901a links to each other, it is connected to the return flow line 160a that is communicated with low voltage side (for example holding vessel).Other structures of regulator 90a are identical with regulator 90 according to the first embodiment of the present invention, therefore omit its detailed description at this.

Describe the work of second embodiment according to the present invention in detail to (d), Figure 12 and Figure 14 hereinafter with reference to Figure 13 (a).The work of main body 19a at first, is described with reference to Figure 13 (a) to (d).Figure 13 (a) to (d) shows the rotor 30a that is in deployed condition.If running shaft 40a drived unit (not shown) clockwise rotates as illustrated in fig. 11, then rotor 30a also turns clockwise.This rotation is corresponding to the rotor 30a linear motion to the left of the expansion shown in Figure 13 (a) to (d).In Figure 13 (a), linear motion part 50a is positioned on the inclined-plane 342a of blade 34a.With reference to Figure 13 (a), the second subspace 112a and the 122a of the first and second space 11a and 12a communicate with each other by suction tank 261a, and the first subspace 111a and the 121a of the first and second space 11a and 12a communicate with each other by drain tank 262a.If rotor 30a rotates with this state, two sub spaces 112a and the 122a that communicates with each other by suction tank 261a can increase so, and thus fluid by sucking with the continuous suction port 2611a of suction pipe (15a sees Figure 11).The fluid that sucks is introduced second subspace 112a and the 122a by suction tank 261a.Simultaneously, the first subspace 111a and the 121a that communicate with each other by drain tank 262a can reduce, and the fluid in two sub spaces 111a and the 121a is discharged to exhaust port 2621a by drain tank 262a.Figure 13 (b) shows when rotor 30a is further rotated, and linear motion part 50a arrives the state of the front end 341a of blade 34a.

With reference to Figure 13 (b), suction tank 261a is positioned on the inclined-plane 342a of blade 34a, and drain tank 262a is positioned on the front end 341a.At this moment, the second subspace 122a of the first space 11a and the second space 12a communicates with each other by suction tank 261a.Drain tank 262a is all linking to each other with the first subspace 121a of the second space 12a on the length.If rotor 30a further with the rotation of this state, then has only the second subspace 122a of the second space 12a to increase, thereby and fluid by sucking with the continuous suction port 2611a of suction pipe (15a sees Figure 12).The fluid that sucks is introduced among the subspace 122a of increase by suction tank 261a.Simultaneously, the first subspace 121a that is provided with drain tank 262a within it of the second space 12a reduces, and the fluid in the first subspace 121a is thus by the exhaust port 2621a discharge continuous with discharge tube (17a sees Figure 12).Figure 13 (c) shows after rotor 30a is further rotated, and linear motion part 50a arrives the state of the front end 341a of blade 34a.

With reference to Figure 13 (c), suction tank 261a and drain tank 262a are positioned on the front end 341a of blade 34a.Suction tank 261a is all linking to each other with the second subspace 122a of the second space 12a on the length, and drain tank 262a is all linking to each other with the first subspace 121a of the second space 12a on the length.If further with the rotation of this state, then the second subspace 122a of the second space 12a increases rotor 30a, and fluid is thus by being inhaled into the continuous suction port 2611a of suction pipe (15a sees Figure 12).The fluid that sucks is introduced among the subspace 122a of increase of the second space 12a.Simultaneously, the first subspace 121a that is connected to drain tank 262a reduces, and the fluid in the 121a of subspace is by the exhaust port 2621a discharge continuous with discharge tube (16a sees Figure 12).Because suction tank 261a and drain tank 262a are positioned at front end 341a simultaneously, so suction tank 261a is not communicated with drain tank 262a.Therefore, the situation that suction port 2611a and 2612a are connected with each other by the first space 11a can not occur, thereby can minimize all losses.Therefore, this can improve the efficient of pump, and because the connection between suction port and the exhaust port can also prevent the backflow of fluid.Therefore do not need the one-way valve (often being called " expulsion valve ") that adds.Figure 13 (d) shows after rotor 30a is further rotated, and linear motion part 50a arrives the state of end points of the front end 341a of blade 34a on angle direction.

With reference to Figure 13 (d), suction tank 261a is positioned on the front end 341a of blade 34a, and drain tank 262a is positioned on the inclined-plane 344a of blade 34a.Suction tank 261a is all linking to each other with the second subspace 122a of the second space 12a on the length.In addition, the first subspace 121a of the first space 11a and the second space 12a communicates with each other by drain tank 262a.If rotor 30a is further with the rotation of this state, the subspace 122a that then is connected to suction tank 262a increases, thereby and fluid by sucking with the continuous suction port 2611a of suction pipe (15a sees Figure 12).The fluid that sucks is introduced among the subspace 122a of the second space 12a then.Simultaneously, space 11a that communicates with each other by drain tank 262a and the subspace 121a of the second space 12a can reduce, and thus the fluid in it by discharging with the continuous exhaust port 2621a of discharge tube (16a sees Figure 12).

When rotor 30a continued rotation, said process repeated by this way, and promptly fluid is constantly sucked by suction port 2611a and discharges by exhaust port 2621a.

By the aforesaid operations of main body 19a, the fluid of discharge is introduced regulator 90a by discharge tube 16a.With reference to Figure 12, the position that the moving element 92a of the discharge capacity regulon 91a of regulator 90a is extremely approached most discharge route 150a by the pushed down of elastic member 93a.In this state, the opening/closing part 921a sealing of inlet 9041a and outlet 9043 9043a passive movement parts 92a.Thus, because main body 19a is discharged by discharge route 150a through second channel 102a by the fluid that discharge tube 16a discharges, be 100% so discharge the amount of fluid.In addition, the moving element 92a of compression unit 96a is in the state that the hydrodynamic pressure that is discharged among the passage 150a is slightly released discharge route 150a.If the hydrodynamic pressure among the discharge route 150a increases with this state, then the hydrodynamic pressure of Zeng Jiaing makes the moving element 92a of discharge capacity regulon 91a resist the power of elastic member 93a away from discharge route 150a, as shown in figure 14.With reference to Figure 14, the position of the opening/closing part 921a of the moving element 92a of discharge capacity regulon 91a allows entrance and exit 9041a and 9043a to open.Therefore, because discharge by the return flow line 160a that is connected to low voltage side by the fluid that discharge tube 16a discharges, be 0% so discharge the amount of fluid from main body 19a.At this moment, one-way valve 94a can prevent that the high-pressure liquid among the discharge route 150a from refluxing.If the hydrodynamic pressure among the discharge route 150a is less than the state shown in Figure 14, then the moving element 92a of discharge capacity regulon 91a is promoted by elastic member 93a and moves with the FLUID TRANSPORTATION that will discharge by discharge tube 16a to discharge route 150a, can increase the amount of discharge fluid thus.At this moment, the moving element 97a of compression unit 96a is pushed open by elastic member 98a, and the FLUID TRANSPORTATION that will be retained among the voltage supply passage 152a arrives in the discharge route 150a.Therefore, the pressure that descends in the discharge route 150a rises to specified point again.

Though

main body

19 and 19a are described as using in pump in above-mentioned two embodiments, the present invention is not limited to this.Ability is appreciated that in the technician

main body

19 and 19a can be constructed to use in fluid power motor.In the main body 19 of first embodiment, when high-pressure liquid is introduced in the rotating rooms 23 by first and

second suction ports

2611 and 2631, thereby rotor 30 rotations and the fluid that is introduced into are discharged by first and

second exhaust ports

2621 and 2641.

In above-mentioned two embodiments, the border width of each contact segment of blade (angular breadth) is described to greater than the maximum angular distance between two adjacent grooves.Yet the present invention is not limited to this.The border width of each contact segment of blade can be formed less than the maximum angular distance between two adjacent grooves.If necessary, each contact segment can be formed with the first and second wall surface lines of rotating room and contact (line contact), rather than the surface contact.Like this, it will be understood by those skilled in the art that and to construct pump by one-way valve is installed, to prevent the fluid reflux in each discharge tube.

Figure 15 to 17 is views of the main body of the oil hydraulic pump of the 3rd embodiment according to the present invention.With reference to Figure 15 to 17, suction pipe 15b is bifurcated and enters successively in two passages that are connected with the side of the alar part 28 of two the end wall 22b of casing 20b and 24b.Discharge tube 16b also is bifurcated and enters successively in two passages that are connected with the side of the guided portion 28b of two the end wall 22b of casing 20b and 24b.Except casing 20b does not have suction tank 261a, drain tank 262a and is positioned at the through hole 282a at guided portion 28b two ends, described casing 20b is identical at the casing 20b of the oil hydraulic pump of textural and above-mentioned second embodiment.Therefore omit its detailed description at this.

With reference to Figure 16 and 17, linear motion part 50b has the linear motion part 50 essentially identical structures with first embodiment shown in Fig. 5.Linear motion part 50b comprises two contact component 58b, and it is installed in the relative position among two retaining wall 54b and the 56b slidably respectively, and slides against the blade (not shown).Each retaining

wall

54b and 56b are provided with receiving groove 511b, the through hole 512b that is communicated with receiving groove 511b and the connecting groove 59b that contact component 58 is installed in it.In the opposite end of two

retaining wall

54b and 56b, the part that receiving groove 511b faces with each other is open, and at upper end 541b and the 561b of two

retaining wall

54b and 56b, receiving groove 511b also is upwards open.The discharge side of retaining

wall

54b and 56b is formed with through hole 512b, to be communicated with each receiving groove 511b.The high-pressure liquid of discharging side provides to receiving groove 511b by through hole 512b.The suction side of retaining

wall

54b and 56b is formed with connecting groove 59b.Each connecting groove 59b connects the two ends of each retaining wall 54b and 56b.The low-pressure fluid of suction side provides to guiding channel 281b by connecting groove 59b, so that linear motion part 50b moves reposefully.

Each is installed to the relative end of contact component 58b of receiving groove 511b towards its end convergent, with the contact jaw 542b or the 546b that form and the blade (not shown) closely contacts.The opposite side of each contact component 58b has the extension, upper and lower, admits the high-pressure liquid of introducing from the respective through hole 512b of each retaining

wall

54b and 56b so that the space to be provided.The high-pressure liquid of introducing from the through hole 512b of retaining

wall

54b and 56b promotes contact component 58b, thereby the contact jaw 542b of contact component closely contacts with the blade (not shown) slidably with 562b.The part of contact component that is connected to the upper end of retaining

wall

54b and 56b also contracts towards its end awl, thereby closely contacts slidably with the outer circumferential face of wheel hub (not shown).Because other work is identical with second embodiment shown in Figure 11 with effect, therefore omit its detailed description at this.

By structure of the present invention, can realize above-mentioned all purposes of the present invention.Especially, because rotor is not eccentric, does not therefore produce vibration and bearing and be not easy to damage.In addition, because blade does not have the structure that moves into and shift out rotor, so its structure is simplified.Especially, because the whole fluids in two spaces that blade separates are to discharge on the contrary with the disclosed pump of Korean Patent No.315954, the amount of therefore discharging fluid has increased by one times.In addition, because the width of constricted zone is maintained fixed, so the fluid of time per unit discharging certain amount, thereby minimize pulsation and stable discharge pressure is provided.In addition, in structure, do not need under the situation of expulsion valve (one-way valve), can easily in fluid power motor, realize conversion.

Though invention has been described in conjunction with exemplary of the present invention, should be appreciated that, under the situation that does not deviate from the spirit and scope of the present invention, can carry out various variations, modification and interpolation to it.

Claims

1. oil hydraulic pump comprises:

The rotating room by the first and second relative wall surfaces, and is used for interconnective the 3rd cylindrical wall of described first and second wall surfaces surface is limited;

Rotor, around the spin axis rotation of passing the described first and second wall surface centers in the described rotating room, and comprise wheel hub and blade with outer circumferential face, described blade is outstanding by the described outer circumferential face radially outward of described wheel hub, and have the outside longitudinal end that closely contacts slidably with described the 3rd wall surface of described rotating room, described blade further comprises the front end that closely contacts slidably with the described first wall surface of described rotating room, the rear end that closely contacts slidably with described second wall surface of described rotating room, and the inclined-plane that connects described front end and described rear end; And

A pair of retaining wall, with described blade collaborative work, and rotation linear motion according to described rotor, each described retaining wall has the opposite edges that face with each other, the described opposite edges of described retaining wall closely contact slidably with two side surfaces, and other edges that described retaining wall is adjacent with described opposite edges closely contact slidably with the outer circumferential face of the wheel hub of described rotor;

Wherein, be provided with the exhaust port that is used to suck the suction port of fluid and is used to discharge fluid with described a pair of retaining wall position adjacent, described a pair of retaining wall is inserted between described suction port and the exhaust port.

2. oil hydraulic pump according to claim 1, wherein said a pair of retaining wall forms as one each other.

3. oil hydraulic pump according to claim 1, wherein, described the 3rd wall surface of described rotating room is provided with suction tank and drain tank, described suction tank is adjacent with described a pair of retaining wall and be connected to described suction port, being connected to each other by two spaces that described blade is separated, described drain tank is adjacent with described a pair of retaining wall and be connected to described exhaust port, being connected to each other by two spaces that described blade is separated.

4. oil hydraulic pump according to claim 3, wherein, the described front-end and back-end of described blade are formed with the described first and second wall surface faces of described rotating room and contact, and the width of the described longitudinal end of the front-end and back-end of each described blade is formed greater than the ultimate range between corresponding described suction tank and the drain tank.

5. oil hydraulic pump according to claim 1, further comprise first and second pressing plates, described first and second pressing plates limit described first and second wall surfaces of described rotating room, and along described spin axis linear motion, and closely contact slidably with the described front-end and back-end of described blade by external force.

6. oil hydraulic pump according to claim 5, wherein said pressing plate is pushed described rotating room to by on high-tension side fluid.

7. oil hydraulic pump according to claim 5, wherein said pressing plate is pushed described rotating room to by elastic member.

8. according to any described oil hydraulic pump in the claim 1 to 7, further comprise regulator, be used to regulate discharge from described exhaust port and provide to the pressure of the fluid of load side.

9. oil hydraulic pump according to claim 8, wherein, the fluid of discharging from described exhaust port flows to the return flow line that is communicated with low voltage side by first and second branched bottoms respectively, and the discharge route that is communicated with load side; And described regulator comprises the discharge capacity regulon, and described discharge capacity regulon has according to the hydrodynamic pressure in described discharge route motion opening and closing the moving element of described first passage, and is arranged on the one-way valve in the described second channel.

10. oil hydraulic pump according to claim 9, wherein said regulator further comprises elastic member, is used for the described fluid of described discharge route described moving element applied pressure side being promoted described moving element in the opposite direction.

11. according to any described oil hydraulic pump in the claim 1 to 7, wherein be provided with two front ends, two rear ends and two pairs of retaining walls, and be provided with suction and drain tank with described two pairs of retaining wall position adjacent, described suction and drain tank are separated by described two pairs of retaining walls.

12. oil hydraulic pump according to claim 11 further comprises regulator, is used to regulate from described exhaust port discharge and provide hydrodynamic pressure to load side.

13. oil hydraulic pump according to claim 12, wherein, the direction of flow of discharging by described two exhaust ports that are positioned at described drain tank is connected to first and second passages of the return flow line that is communicated with low voltage side, and the flow direction is connected to third and fourth passage of the discharge route that is communicated with load side, and described regulator comprises the discharge capacity regulon, and described discharge capacity regulon has according to the hydrodynamic pressure in described discharge route motion to open and close described first or the moving element of second channel respectively, and be arranged on first and second one-way valves in described third and fourth passage.

14. oil hydraulic pump according to claim 13, wherein said regulator further comprises elastic member, is used for the fluid of described discharge route the described moving element side of exerting pressure being promoted described moving element in the opposite direction.

15. according to any described oil hydraulic pump in the claim 9,19 and 12 to 14, wherein said regulator further comprises the accumulation part.

16. oil hydraulic pump according to claim 15, wherein, described accumulation part comprises the moving element that moves by the hydrodynamic pressure that receives in the described discharge route, and the elastic member that promotes described moving element on the direction opposite with the hydrodynamic pressure that is applied to described moving element.

17. according to any described oil hydraulic pump in the claim 1 to 7, wherein, described a pair of retaining wall has and the contacted contact component of the both side surface of described blade, and in the described a pair of retaining wall each is provided with and is used to hold the receiving groove of described contact component and is used to make described receiving groove and discharges the through hole that side is communicated with.

18. a fluid power motor comprises:

Rotor, around the spin axis rotation of passing the described first and second wall surface centers in the described rotating room, and comprise wheel hub and blade with outer circumferential face, described blade is outstanding from the described outer circumferential face radially outward of described wheel hub, and have the outside longitudinal end that closely contacts slidably with described the 3rd wall surface of described rotating room, described blade further comprises the front end that closely contacts slidably with the described first wall surface of described rotating room, the rear end that closely contacts slidably with described second wall surface of described rotating room, and the inclined-plane that connects described front end and described rear end; And

Wherein, be provided with inlet that is used for incoming fluid and the outlet that is used for effluent fluid in the position adjacent to described a pair of retaining wall, described a pair of retaining wall is inserted between described inlet and the described outlet.

19. fluid power motor according to claim 18, wherein said a pair of retaining wall forms as one each other.

20. fluid power motor according to claim 18, wherein, described the 3rd wall surface of described rotating room is provided with and flows into groove and spout, described inflow groove is adjacent with described a pair of retaining wall and be connected to described inlet, being connected to each other by each space that described blade is separated, described drain tank is adjacent with described a pair of retaining wall and be connected to described outlet, being connected to each other by each space that described blade is separated.

21. fluid power motor according to claim 20, wherein, the described front-end and back-end of described blade are formed with the described first and second wall surface faces of described rotating room and contact, and the width of the described longitudinal end of the front-end and back-end of each described blade is formed greater than the ultimate range between corresponding described suction tank and the drain tank.

22. fluid power motor according to claim 18, further comprise first and second pressing plates, described first and second pressing plates form described first and second wall surfaces of described rotating room, and along described spin axis linear motion, and closely contact with the described front-end and back-end of described blade by external force.

23. fluid power motor according to claim 22, wherein said pressing plate is pushed described rotating room to by on high-tension side fluid.

24. fluid power motor according to claim 22, wherein said pressing plate is pushed described rotating room to by elastic member.