WO2006090516A1 - ポンプロータ - Google Patents
ポンプロータ Download PDFInfo
- Publication number
- WO2006090516A1 WO2006090516A1 PCT/JP2005/020803 JP2005020803W WO2006090516A1 WO 2006090516 A1 WO2006090516 A1 WO 2006090516A1 JP 2005020803 W JP2005020803 W JP 2005020803W WO 2006090516 A1 WO2006090516 A1 WO 2006090516A1
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- WO
- WIPO (PCT)
- Prior art keywords
- pump rotor
- rotors
- fluid
- pump
- less
- Prior art date
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2/00—Rotary-piston machines or pumps
- F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2/00—Rotary-piston machines or pumps
- F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C2/082—Details specially related to intermeshing engagement type machines or pumps
- F04C2/084—Toothed wheels
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2/00—Rotary-piston machines or pumps
- F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
- F04C2/102—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member the two members rotating simultaneously around their respective axes
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B30—PRESSES
- B30B—PRESSES IN GENERAL
- B30B11/00—Presses specially adapted for forming shaped articles from material in particulate or plastic state, e.g. briquetting presses, tabletting presses
- B30B11/005—Control arrangements
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2230/00—Manufacture
- F04C2230/20—Manufacture essentially without removing material
- F04C2230/22—Manufacture essentially without removing material by sintering
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
- F05C2201/00—Metals
- F05C2201/04—Heavy metals
- F05C2201/0469—Other heavy metals
- F05C2201/0475—Copper or alloys thereof
Definitions
- the present invention relates to a pump rotor used in an internal gear pump that sucks and discharges fluid by changing the volume of a cell formed between tooth surfaces of an inner pump rotor and an outer pump rotor.
- the internal gear pump has an inner pump rotor with external teeth formed thereon, an outer pump rotor with internal teeth that mesh with the external teeth, a suction port through which fluid is sucked, and fluid is discharged. And a casing formed with a discharge port that conveys the fluid by sucking and discharging the fluid due to the volume change of the cell formed between the tooth surfaces of the rotors when the rotors rotate together. It is configured.
- the two rotors are configured to squeeze and rotate while the inner surfaces of the casing, both end surfaces of the rotors in the rotation axis direction and the outer peripheral surface of the outer pump rotor are in sliding contact with each other.
- such an inscribed gear pump is generally disposed between a supply destination (for example, a cylinder head) of a fluid (for example, a lubricating oil) and an oil pan in which the fluid is stored.
- the tangential gear pump is configured to communicate with the oil pan through a strainer. Then, when the inscribed gear pump is driven, the fluid in the strainer force oil pan is supplied to the inside of the inscribed gear pump, and the fluid is sucked by the change in the volume of the cell as described above. By discharging, fluid is supplied to the cylinder head and the like.
- Patent Document 1 Japanese Patent Laid-Open No. 11-343985
- the present invention has been made in view of these problems, and an object thereof is to provide a pump rotor having improved seizure resistance. Means for solving the problem
- a pump rotor of the present invention includes an inner one-side pump rotor in which external teeth are formed, and an outer-side pump rotor in which internal teeth that mesh with the external teeth are formed.
- the present invention at the time of driving the internal gear pump, at least the outer peripheral surface of the outer pump rotor and the both end surfaces orthogonal to the rotation shafts of the two rotors are in sliding contact with the inner surface of the casing.
- a part of the fluid can be held in a minute hole opened in the cut surface, and so to speak, a part of the fluid can be infiltrated into the outer peripheral surface and the surface layer portions of both end surfaces. Therefore, when this inscribed gear pump is stopped and then restarted, a part of the fluid is separated from the inner surface of the casing, the outer peripheral surface of the outer pump rotor, and the both end surfaces of the two rotors. Therefore, the seizure resistance of the pump rotor can be improved.
- the compressive force is also formed by a pump rotor force Fe-Cu-C-based sintered material with a density of 6.6 gZcm 3 or more and 7. lgZcm 3 or less. It becomes possible to secure the necessary minimum pressure strength.
- the pump rotor is formed by forming a green compact, firing it, and then applying sizing. The rotor is made of the material and density described above. It is possible to prevent the chamfering amount of the ridge line portion from being increased by crushing the intersecting ridge line portion between the both end surfaces and the tooth surface of the pump rotor at the time of the saizinkae.
- the cell partitioned by the tooth surface and the inner surface of the casing can be provided with high liquid tightness.
- the intersecting ridge line portion between the both end surfaces and the tooth surface has an amount of rise from the end surface in the rotational axis direction of not more than 0. Olmm and is directed from the tooth surface in the radial direction. It is desirable that the amount of protrusion is 0.05 mm or less.
- the intersecting ridge line portion is formed with the rising amount and the protruding amount, in the internal gear pump having this pump rotor, the intersecting ridge line portion is brought into contact with the inner surface of the casing. It becomes possible. As a result, the cell is partitioned by the intersecting ridge portion, the tooth surface, and the inner surface of the casing, so that the cell can be provided with high liquid-tightness, and when the internal gear pump is driven. The fluid in the cell can be reliably prevented from leaking between the both end surfaces and the inner surface of the casing.
- the cross ridge line portion of the both end surfaces is in sliding contact with the inner surface of the casing in a limited manner. It is easy to wear out, and it is possible to avoid shortening the life of the inscribed gear pump.
- the crossed ridge line portions are in contact with each other at the outer teeth and the inner teeth at the time of the meshing, but the center portions in the thickness direction of both rotors are in contact with each other. It becomes possible to avoid being out of contact. As a result, the individual cells can be reliably partitioned in the circumferential direction, and a decrease in fluid conveyance performance can be avoided.
- the seizure resistance of the pump rotor can be improved.
- FIG. 1 is a cross-sectional plan view of an internal gear pump having a pump rotor shown as an embodiment according to the present invention.
- FIG. 2 is a cross-sectional view of the inscribed gear pump shown in FIG.
- FIG. 3 is an enlarged view of the inscribed gear pump shown in FIG.
- FIG. 4 is (a) an enlarged sectional view of the outer peripheral surface of the outer pump rotor or both end surfaces of the outer pump rotor and the inner pump rotor shown as one embodiment according to the present invention, and (b).
- FIG. 6 is an enlarged cross-sectional view of an outer peripheral surface of an outer pump rotor shown as a conventional example according to the present invention, or both end surfaces of an outer pump rotor and an inner pump rotor.
- FIG. 5 is a cross-sectional view illustrating an embodiment of a main part of a powder molding apparatus for forming the pump rotor shown in FIG. 1, and illustrating a filling process.
- FIG. 6 is a view showing a lower punch raising process in the process of retracting the show box in the powder molding apparatus shown in FIG.
- FIG. 7 is a cross-sectional view showing a main part of the powder molding apparatus in a state where the lower punch is lowered from the state shown in FIG. 6 and filling of the raw material powder is completed.
- FIG. 8 shows the main parts of the powder molding apparatus shown in FIGS. 5 to 7, in which (a) a mechanical drive process for lowering the upper punch to the bottom dead center, and (b) the thickness of the cavity is the molding target.
- FIG. 6 is a cross-sectional view showing an adjusting step for raising the lower punch until the thickness is reached, and (c) a step for extracting the formed green compact from the die.
- Fig. 9 is a diagram showing the results of verifying the operational effects of the pump rotor shown as an embodiment according to the present invention.
- FIG. 10 shows another embodiment of the main part of the powder molding apparatus for forming the pump rotor shown in FIG.
- the rotors 20 and 30 are connected to the inner surface 50a of the casing 50 and both end surfaces in the direction of the rotation axes 01 and 02 of the rotors 20 and 30, in other words, both end surfaces 20a and 30a orthogonal to the rotation axes 01 and 02.
- the outer side pump rotor 30 is rotated while being in sliding contact with the outer peripheral surface 30b.
- a plurality of cells C are formed between the tooth surfaces of the inner-side pump rotor 20 and the outer-side pump rotor 30 along the rotational direction of the two-port motors 20, 30.
- Each cell C is individually partitioned by the outer teeth 21 of the inner pump rotor 20 and the inner teeth 31 of the outer pump rotor 30 coming into contact with each other on the front and rear sides in the rotational direction of the two ports 20 and 30.
- both sides of the powerful side are partitioned by the inner surface of the casing 50, thereby forming an independent fluid transfer chamber.
- Cell C rotates with the rotation of both rotors 20 and 30 and repeats the increase and decrease in volume with one rotation as one cycle.
- the casing 50 is provided with a suction port 51 that communicates with the cell C when the volume increases, and a discharge port 52 that communicates with the cell C when the volume decreases, from the suction port 51 to the cell C.
- the sucked fluid is transported as the rotors 20 and 30 are rotated and discharged from the discharge port 52.
- the rotors 20 and 30 of the present embodiment include Fe C Cu-based sintered containing at least 1 wt% to 4 wt% Cu, and 0.2 wt% to 1. Owt% at least.
- Cu if it is less than 1%, the solid solution strengthening (hardness and strength) of Fe becomes insufficient, and if it exceeds 4%, expansion during sintering increases, making it difficult to form a rotor with high precision. become.
- the rotors 20 and 30 have a density of 6.6 gZcm 3 or more and 7. lgZcm 3 or less, and at least the outer peripheral surface 30b of the outer pump rotor 30 and the rotors 20, 30 Both end faces 20a and 30a in the 30 rotation axis 01 and 02 directions are non-ground surfaces, and their ten-point average roughness Rz is 4 m or more and 10 m or less. Further, the rotors 20 and 30 have a porosity of 10% or more and 20% or less.
- the total force on the outer surface of each of the two ports 20, 30 including the both end surfaces 20a, 30a and the outer peripheral surface 30b is an unground surface, and the ten-point average roughness Rz is within the above range.
- the variation in the distance (thickness) R1 between the both end faces 20a, 20a and between the end faces 20a, 30a in each of the rotors 20, 30 is 0.02 mm or more over the entire area of each end face 20a, 30a. It is within the range of 10mm or less.
- the variation of the outer diameter R2 of the outer pump rotor 30 is within the range of 0.06 mm or more and 0.15 mm or less.
- the difference between the inner diameter of the casing inner surface 50a and the outer diameter R2 of the outer pump rotor 30 is 0.06 mm or more and 0.35 mm or less.
- the difference between the rotors 20 and 30 and the thickness R1 is 0.02 mm or more and 0.10 mm or less.
- the intersecting ridge line portions 20c and 30c between the both end surfaces 20a and 30a and the tooth surface are rotated from the end surfaces 20a and 30a to the rotation axis O.
- the rising amount Y in the direction of 1, 02 is set to 0.01 mm or less
- the protruding amount Z from the tooth surface in the radial direction is set to 0.05 mm or less.
- each of the intersecting ridge line portions 20c and 30c has a rising amount Y and a protruding amount Z within the above ranges, and the inner side pump rotor 20 is convex in a curved shape radially outward, and the outer side pump rotor 3 In the case of 0, the surface is convex inward in the radial direction.
- Both rotors 20 and 30 are to compact a powder to form a green compact, then fire the green compact, and then sizing the green compact, and further remove the flash that has undergone surface grinding. Is obtained.
- the method for forming the green compact will be described.
- reference numeral 110 is an upper punch
- reference numeral 120 is a lower punch
- reference numeral 130 is a core rod
- reference numeral 140 is a die
- reference numeral 150 is a shoe box
- reference numeral 160 is a measuring hand for measuring a distance between both punches.
- P is raw material powder.
- the die 140 is provided with a molding hole, and a core rod 130 is arranged at the center of the molding hole.
- the cylindrical space formed between the forming hole and the core rod 130 is closed by a cylindrical lower punch 120 in which a downward force is also fitted and a cylindrical upper punch 110 in which an upward force is also fitted. It is said.
- the raw material powder P is pressurized in the cavity 100a to form a green compact Z1 (FIG. 8) along the shape of the cavity 100a.
- the shear box 150 in which the powder 100a is filled with the raw material powder P, is formed in a box shape with the lower surface open, and the front and back are in contact with the upper surface of the die 140 (the horizontal direction in the figure). ).
- the raw box P is supplied with raw material powder P from a hopper (not shown) inside the shelf box 150. The raw box P moves forward to the position shown in FIG. Powder P is dropped into the cavity 100a and filled.
- the upper punch 110 is fixed to the upper punch holding member 110A held so as to be vertically movable with respect to the base 100b via the frame 170, and can move up and down integrally with the upper punch holding member 110A. Become! /
- the upper punch holding member 11 OA to which the upper punch 110 is fixed is mechanically driven up and down by a mechanism (primary drive device) such as a crank mechanism, a knuckle press, or a cam mechanism, and descends the upper punch 110 to the bottom dead center. By doing so, the raw material powder P filled in the cavity 100a can be pressurized.
- a mechanism primary drive device
- the lower punch 120 is fixed to the lower punch holding member 120A, and moves up and down integrally with the lower punch holding member 120A by the piston 181 of the fluid pressure cylinder (secondary drive device) 180 fixed to the base 100b. I am able to do that. Between the lower punch 120 (lower punch holding member 120A) and the base 100b, the lower punch 120 relative to the base 100b is provided.
- a filling amount correcting linear scale 161 for detecting the position of is attached.
- the control unit 190 that has received the detection signal from the filling amount correcting linear scale 161 controls the flow rate in the fluid pressure cylinder 180 so that the piston 181, that is, the lower punch 120 can be moved to an arbitrary position. Become.
- the bottom dead center correcting linear scale (measuring means) 160 is attached between the upper punch holding member 110A and the lower punch holding member 120A, and the upper punch holding member 110A and the lower punch holding member are fixed.
- a measurement value obtained by measuring the distance from the holding member 120A, that is, the distance between the upper punch 110 and the lower punch 120 is output as a signal.
- a target value is set in advance in the control unit 190 to which this signal is input, and the measured value force can be controlled so that the flow rate in the fluid pressure cylinder 180 becomes the target value.
- the target value is such that the thickness of the cavity 100a becomes the molding target thickness between the upper punch 110 and the lower punch 120.
- the control unit 190 is also supplied with a show box position detection signal that is output from a show box position detection sensor (not shown) and indicates the position of the show box 150.
- the upper punch 110, the lower punch 120, and the die 140 are respectively arranged at initial positions.
- the shelf box 150 is moved forward (advance process), opened on the cavity 100a as shown in FIG.
- the shoe box 150 advances from the rear (right side of FIG. 5) to the front (left side of FIG. 5) and moves to the position shown in FIG. Open and force also opens on the front side. Therefore, the cavity 100a is opposed to the opening of the shoe box 150 for a long time on the rear side, and the raw material powder P is filled with higher density toward the rear side.
- the lower punch 120 is raised with respect to the die 140 at the initial stage of the retracting process while retracting the shoe box 150 to retract from the cavity 100a (the retracting process). .
- a part of the raw material powder P filled in the rear side of the cavity 100a is pushed up on the die 140 and removed by the shout box 150 at the same time by raising the lower punch 120 after retreating from the front side of the 100a. And correct the amount of raw material powder P filled in the cavity 100a at the front and rear.
- the volume of the raw material powder P increases on the front side of the cavity 100a, and the volume of the raw material powder P decreases on the rear side of the cavity 100a.
- the raised lower punch 120 is lowered with respect to the die 140 and returned to the initial position.
- the raw material powder P on the front side of the cavity 100a pushed up on the die 140 is returned to the inside of the cavity 100a (inside the die 140), and the filling height of the raw material powder P in the cavity 100a is greatly increased on the front side. Smaller on the side.
- the filling height of the raw material powder P is increased on the low density front side, and is reduced on the high density rear side, thereby reducing the non-uniform filling amount due to the forward / backward direction of the syubox 150.
- the entire powder 100a is uniformly filled with raw material powder P.
- Fig. 8 shows the process of pressure molding performed by driving the upper and lower punches.
- the upper punch 110 is lowered to the bottom dead center (mechanical movement limit position), and the raw material powder P in the cavity 100a is compressed.
- the punch 110 can actually reach the ideal bottom dead center because of the stagnation of the force device designed to lower the top punch 110 to the ideal bottom dead center. Absent.
- the ideal bottom dead center of the upper punch 110 forms a cavity 100a having a thickness that is, for example, about lmm larger than the molding target thickness of the green compact, with the lower punch 120 fixed at the initial position. It is set to be. In other words, even if the device does not stagnate or stretch, even if the upper punch 110 is lowered to the ideal bottom dead center, the thickness of the cavity 100a is larger than the molding target thickness and is thicker than the molding target thickness. Small green compacts are never formed. [0036] (Secondary driving process)
- the fluid pressure cylinder 180 is driven to initialize the lower punch 120.
- the positional force is also increased until the thickness of the cavity 100a reaches the molding target thickness.
- the movement of the lower punch 120 at this time is performed by feeding back the measured value by the bottom dead center correcting linear scale 160.
- control unit 190 that has received the detection signal from the filling amount correction linear scale 161 controls the flow rate of the fluid pressure cylinder 180, and the bottom dead center correction linear scale 160 has both punches 110, 120.
- the control unit 190 drives and controls the fluid pressure cylinder 180 to raise the lower punch 120 until the value reaches the molding target thickness.
- the upper punch 110 may be slightly pushed up by raising the lower punch 120.
- the lower punch 120 is raised by feeding back the measured value of the distance between the two punches 110, 120, The lower punch 120 is driven until the thickness of the cavity 100a reaches the molding target thickness, and the lowering deficiency of the upper punch 110 is corrected, and the thickness of the green compact can be set as the target value.
- the upper punch 110 is raised, the core rod 130 and the die 140 are lowered with respect to the lower punch 120, and the formed green compact Z1 is put into the die 140. Extract from it. Further, the lower punch 120 raised in the secondary driving process is returned to the initial position to prepare for forming the next green compact.
- the green compact Z1 is fired, it is corrected by applying a side effect by a well-known method, and then subjected to deburring without surface grinding.
- the side pump rotor 20 and the outer side pump rotor 30 are formed.
- the pump rotors 20 and 30 at the time of driving the internal gear pump 10, at least the one-side pump that is in sliding contact with the inner surface 50a of the casing 50.
- the outer peripheral surface 30b of the rotor 30 and both end surfaces 20a and 30a in the directions of the rotational axes 01 and 02 of the rotors 20 and 30 are non-ground surfaces, and the ten-point average roughness Rz is 4 / zm to 10 / zm, when the inscribed gear pump 10 is driven and then stopped, a part of the fluid sucked into the interior at the time of driving is at least the outer peripheral surface 30b and It can be held on both end faces 20a, 30a.
- the both rotors 20, 30-force Fe-Cu-C-based sintered material is formed with a density of 6.6 gZcm 3 or more and 7. lgZcm 3 or less. It becomes possible to ensure the minimum necessary breaking strength and surface pressure strength of the rotors 20 and 30, and at the time of the sizing, the intersecting ridge portions 20c and 30c of the rotors 20 and 30 are crushed, It becomes possible to suppress the chamfering amount of the ridge lines 20c and 30c from increasing.
- the inscribed gear pump 10 when the inscribed gear pump 10 is driven, it is possible to suppress leakage between the end surfaces 20a, 30a and the casing inner surface 50a from the fluid force intersecting ridge portions 20c, 3 Oc in the cell C.
- the cell C partitioned by the intersecting ridge portions 20c and 30c, the tooth surface, and the casing inner surface 50a can have high liquid-tightness.
- the intersecting ridge portions 20c and 30c are not chamfered during the sizing process, and the rising amount Y from the end surfaces 20a and 30a toward the rotation axes 01 and 02 is 0.01.
- the crossed ridge portions 20c and 30c are connected to the casing inner surface 50a. It becomes possible to make it contact
- the cell C is partitioned by the intersecting ridge line portions 20c, 30c, the tooth surface, and the casing inner surface 50a, so that the cell C can be provided with high liquid-tightness.
- the mold gear pump 10 is driven, the fluid force in the cell C can be prevented from leaking between the both end faces 20a, 30a and the casing inner face 50a. Therefore, the fluid transfer performance of the inscribed gear pump 10 can be improved.
- the crossed ridge line portions 20c and 30c come into contact with each other at the outer teeth 21 and the inner teeth 31 at the time of the meshing. It is possible to avoid that the center portions in the thickness direction of the data 20 and 30 do not contact each other. As a result, the individual cells C can be reliably partitioned in the circumferential direction, and a decrease in fluid transport performance can be avoided.
- both rotors 20 and 30 are formed based on the green compact Z1 formed by the powder forming apparatus 100 shown in FIGS. 5 to 8, the sizing process is performed. It is possible to prevent the accuracy of the size of the rotors 20 and 30 in the directions of the rotational axes 01 and 02, that is, the thickness, from being reduced without grinding the end faces 20a and 30a. Become. Therefore, it is possible to eliminate the grinding process from the process of manufacturing the rotors 20 and 30, and the rotors 20 and 30 having improved seizure resistance can be highly efficient without reducing accuracy. Can be formed.
- specimens used for this test there are two types of specimens used for this test, one that has been ground after the sizing process and one that has not been ground after the sizing process. It is formed into a disk shape with Fe-C-Cu-based sintered material containing at least wt% to 2.5% and 0.6% to 0.75 wt%, and the density and surface roughness for each of these types.
- Fe-C-Cu-based sintered material containing at least wt% to 2.5% and 0.6% to 0.75 wt%, and the density and surface roughness for each of these types.
- seizure resistance refers to the test piece placed on the surface of a plate-like test material (surface roughness 3.2 Rz) that also becomes an FC material, and each of the test piece and the test material. While supplying lubricating oil between the contact surfaces, rotate the specimen around its axis at a peripheral speed of approximately 3. lmZs. In this process, a load was gradually applied to the test piece in the thickness direction, and the load when seizure occurred on the contact surface of the test piece was measured. Then, the load was divided by the area of the contact surface of the test piece, and this value was used as a seizure resistance load.
- the number of teeth of the external teeth 21 and the internal teeth 31 is not limited to the above embodiment.
- the configuration in which the intersecting ridge portions 20c and 30c are respectively convex in the curved shape is shown. However, when C (the chamfering amount) is 0.2 mm or less during the sizing cache, the chamfering is performed. Also good.
- a die 205 having a cavity 200a filled with raw material powder P and an upper punch 208 are driven up and down, and the lower punch 209 is always fixed.
- the die 205 is attached to a lower slider 203 that slides in the lower guide 202 via a lower ram 204, and is moved up and down by driving of driving means (not shown) such as a ball screw mechanism.
- driving means such as a ball screw mechanism.
- a lower punch 209 fixed to the fixing plate 213 is disposed so as to fit a downward force into the cavity 20Oa.
- an upper punch 208 force that can be moved in and out of the cavity 200a. It is arranged coaxially facing the inch 209.
- the upper punch 208 is attached to an upper guide 210 that slides in the upper slider 206 through an upper ram 207 including a hydraulic piston 222 and a hydraulic cylinder 201 to which an upper punch plate 223 is attached.
- the upper slider 206 is connected via a link mechanism 211 to a crankshaft 212 that is rotated by a drive motor M (the next drive device).
- the drive motor M is a servo motor that is stored in the computer (control unit) 220 and is driven and stopped in accordance with a program.
- the upper ram 207 has a hydraulic cylinder 221 fixed to the upper guide 210 and a hydraulic piston 222 attached to the upper punch plate 223.
- the hydraulic cylinder 221 is provided with a hydraulic pressure supply port 221a, and hydraulic pressure is supplied from a hydraulic unit 226 (secondary drive device) via a hydraulic pressure supply pipe 225 connected thereto.
- the hydraulic pressure is controlled by a hydraulic servo valve 224 provided in the hydraulic supply pipe 225 and driven by the computer 220.
- the upper ram 207 is entirely driven up and down by the drive motor (primary drive device) M, and the hydraulic piston 222 is driven up and down by the hydraulic unit (secondary drive device) 226.
- the distance between the upper punch plate 223 and the fixing plate 213 is between the upper punch plate 223 to which the upper punch 208 is fixed and the fixing plate 213 to which the lower punch 209 is fixed.
- a linear scale (measuring means) 214 is provided for measuring. The measurement value of the linear scale 214 is transmitted to the computer 220, and the computer 220 calculates the drive signal of the drive motor M and the drive signal of the hydraulic servo valve 224 based on the measurement value, and outputs them. ! /
- the upper punch 208, the lower punch 209, and the die 205 are arranged in the initial positions in advance.
- the computer 220 stops the drive motor M that mechanically drives the upper ram 207, and the lowering of the upper punch 208 due to the lowering of the upper ram 207 stops. Is done.
- the hydraulic servo valve 224 is driven simultaneously with the lowering of the upper ram 207, and the hydraulic cylinder 221 is driven until the measured value from the linear scale 214 reaches the set value (the value at which the thickness of the cavity 2 OOa becomes the molding target thickness). Then, the hydraulic pressure is supplied to the hydraulic piston 222 and the upper punch 208 is lowered.
- the raw material powder P in the cavity 200a is pressed from both the upper and lower sides, and a uniform pressure is applied. Is received and compressed to a uniform density in the vertical direction.
- the hydraulic servo valve 224 is controlled by the computer 220, the hydraulic piston 222 is raised, the upper punch 208 is raised, and the rotation of the drive motor M is resumed.
- the upper punch 208 is raised together with the upper ram 207, and the die 205 is lowered.
- the green compact molded to the target molding thickness is extracted from the die 205 (cavity 20 Oa) and placed on the lower punch 209.
- a pump rotor with improved seizure resistance can be provided.
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- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
- Details And Applications Of Rotary Liquid Pumps (AREA)
Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US11/816,788 US7632083B2 (en) | 2005-02-22 | 2005-11-14 | Anti-galling pump rotor for an internal gear pump |
EP05806300.9A EP1852611B1 (en) | 2005-02-22 | 2005-11-14 | Pump rotors |
BRPI0520035-0A BRPI0520035A2 (pt) | 2005-02-22 | 2005-11-14 | rotor de bomba |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2005-045461 | 2005-02-22 | ||
JP2005045461A JP2006233771A (ja) | 2005-02-22 | 2005-02-22 | ポンプロータ |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2006090516A1 true WO2006090516A1 (ja) | 2006-08-31 |
Family
ID=36927165
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2005/020803 WO2006090516A1 (ja) | 2005-02-22 | 2005-11-14 | ポンプロータ |
Country Status (8)
Country | Link |
---|---|
US (1) | US7632083B2 (ja) |
EP (1) | EP1852611B1 (ja) |
JP (1) | JP2006233771A (ja) |
KR (1) | KR100956047B1 (ja) |
CN (1) | CN100535441C (ja) |
BR (1) | BRPI0520035A2 (ja) |
MY (1) | MY140145A (ja) |
WO (1) | WO2006090516A1 (ja) |
Families Citing this family (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN101809289B (zh) * | 2007-09-07 | 2015-05-06 | Gkn烧结金属有限公司 | 精密粉末金属部件、组件和方法 |
KR100851291B1 (ko) * | 2008-04-16 | 2008-08-08 | 최광일 | 오일펌프용 기어의 표면가공방법 |
JP2011190763A (ja) * | 2010-03-16 | 2011-09-29 | Denso Corp | 回転式ポンプ |
JP5952723B2 (ja) * | 2012-11-30 | 2016-07-13 | 株式会社日本自動車部品総合研究所 | 回転式ポンプおよびそれを備えたブレーキ装置 |
CN103192071B (zh) * | 2013-04-23 | 2015-03-04 | 南京浩德粉末冶金有限公司 | 液压补油泵内外转子粉末冶金配方及制造方法 |
JP6599181B2 (ja) * | 2015-09-07 | 2019-10-30 | アイシン機工株式会社 | ギヤポンプ |
KR102355730B1 (ko) * | 2016-09-02 | 2022-01-26 | 스택폴 인터내셔널 엔지니어드 프로덕츠, 엘티디. | 이중 입력 펌프 및 시스템 |
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JP2002138968A (ja) * | 2000-08-22 | 2002-05-17 | Schwaebische Huettenwerke Gmbh | らせん状噛み合いを有する歯車ポンプ |
JP2003286970A (ja) * | 2002-03-29 | 2003-10-10 | Aisin Seiki Co Ltd | オイルポンプ |
JP2004197670A (ja) * | 2002-12-19 | 2004-07-15 | Mitsubishi Materials Corp | 内接型オイルポンプ |
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JPS5358807A (en) * | 1976-11-09 | 1978-05-27 | Nippon Piston Ring Co Ltd | Rotary fluid pump |
JPS60147589A (ja) * | 1984-01-13 | 1985-08-03 | Toyooki Kogyo Co Ltd | 液体歯車ポンプ |
JPS60237189A (ja) * | 1984-05-09 | 1985-11-26 | Toyota Motor Corp | ル−ツポンプのロ−タ構造 |
JPH02207187A (ja) * | 1989-02-06 | 1990-08-16 | Hitachi Ltd | スクリュー圧縮機 |
DE4200883C1 (ja) | 1992-01-15 | 1993-04-15 | Siegfried A. Dipl.-Ing. 7960 Aulendorf De Eisenmann | |
DE4401783A1 (de) | 1994-01-21 | 1995-07-27 | Cerasiv Gmbh | Förderaggregat mit einer keramischen Innenzahnradpumpe |
JPH08159044A (ja) * | 1994-12-01 | 1996-06-18 | Mitsubishi Materials Corp | 内接式ギヤポンプ |
JPH10331777A (ja) | 1997-05-28 | 1998-12-15 | Denso Corp | 内接ギヤポンプ |
JPH11343985A (ja) | 1998-05-29 | 1999-12-14 | Suzuki Motor Corp | エンジンのオイルポンプ |
JP2001212618A (ja) * | 2000-02-02 | 2001-08-07 | Hitachi Powdered Metals Co Ltd | 焼結含油軸受の内径面成形用コアロッド |
US6264718B1 (en) * | 2000-05-26 | 2001-07-24 | Kobelco Metal Powder Of America, Inc. | Powder metallurgy product and method for manufacturing the same |
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JP2005344126A (ja) * | 2002-10-04 | 2005-12-15 | Hitachi Powdered Metals Co Ltd | 焼結歯車 |
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JP2005016450A (ja) * | 2003-06-26 | 2005-01-20 | Mitsubishi Materials Corp | 内接型ギヤポンプのインナーロータ |
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-
2005
- 2005-02-22 JP JP2005045461A patent/JP2006233771A/ja active Pending
- 2005-11-11 MY MYPI20055300A patent/MY140145A/en unknown
- 2005-11-14 CN CNB200580048423XA patent/CN100535441C/zh not_active Expired - Fee Related
- 2005-11-14 EP EP05806300.9A patent/EP1852611B1/en not_active Expired - Fee Related
- 2005-11-14 US US11/816,788 patent/US7632083B2/en not_active Expired - Fee Related
- 2005-11-14 BR BRPI0520035-0A patent/BRPI0520035A2/pt not_active Application Discontinuation
- 2005-11-14 WO PCT/JP2005/020803 patent/WO2006090516A1/ja active Application Filing
- 2005-11-14 KR KR1020077019725A patent/KR100956047B1/ko not_active IP Right Cessation
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JP2002138968A (ja) * | 2000-08-22 | 2002-05-17 | Schwaebische Huettenwerke Gmbh | らせん状噛み合いを有する歯車ポンプ |
JP2003286970A (ja) * | 2002-03-29 | 2003-10-10 | Aisin Seiki Co Ltd | オイルポンプ |
JP2004197670A (ja) * | 2002-12-19 | 2004-07-15 | Mitsubishi Materials Corp | 内接型オイルポンプ |
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See also references of EP1852611A4 * |
Also Published As
Publication number | Publication date |
---|---|
EP1852611A4 (en) | 2013-10-30 |
JP2006233771A (ja) | 2006-09-07 |
US7632083B2 (en) | 2009-12-15 |
KR100956047B1 (ko) | 2010-05-06 |
BRPI0520035A2 (pt) | 2009-04-14 |
EP1852611A1 (en) | 2007-11-07 |
CN101124407A (zh) | 2008-02-13 |
EP1852611B1 (en) | 2014-11-05 |
MY140145A (en) | 2009-11-30 |
CN100535441C (zh) | 2009-09-02 |
US20080213117A1 (en) | 2008-09-04 |
KR20070107081A (ko) | 2007-11-06 |
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