WO2017187928A1 - Pompe composite - Google Patents

Pompe composite Download PDF

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Publication number
WO2017187928A1
WO2017187928A1 PCT/JP2017/014433 JP2017014433W WO2017187928A1 WO 2017187928 A1 WO2017187928 A1 WO 2017187928A1 JP 2017014433 W JP2017014433 W JP 2017014433W WO 2017187928 A1 WO2017187928 A1 WO 2017187928A1
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WO
WIPO (PCT)
Prior art keywords
pump
pump unit
composite
rotor
housing
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2017/014433
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English (en)
Japanese (ja)
Inventor
竹花　憲夫
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mikuni Corp
Original Assignee
Mikuni Corp
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Filing date
Publication date
Application filed by Mikuni Corp filed Critical Mikuni Corp
Publication of WO2017187928A1 publication Critical patent/WO2017187928A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M1/00—Pressure lubrication
    • F01M1/02—Pressure lubrication using lubricating pumps
    • 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
    • F04C11/00—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations
    • 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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/06—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • 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
    • 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
    • F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
    • F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member

Definitions

  • the present invention relates to a pump that is applied to a lubrication system such as an engine or transmission and supplies lubricating oil, and more particularly to a composite pump that combines a trochoid pump and a vane pump.
  • Conventional compound pumps include a trochoid pump consisting of a housing, an inner rotor and an outer rotor, a trochoid pump drive shaft, a vane pump including a cam rotor and a plurality of vanes, a vane pump drive shaft, and a vane pump drive shaft as a trochoid pump drive shaft.
  • a trochoid pump consisting of a housing, an inner rotor and an outer rotor, a trochoid pump drive shaft, a vane pump including a cam rotor and a plurality of vanes, a vane pump drive shaft, and a vane pump drive shaft as a trochoid pump drive shaft.
  • a trochoid pump consisting of a housing, an inner rotor and an outer rotor, a trochoid pump drive shaft, a vane pump including a cam rotor and a plurality of vanes, a vane pump drive shaft, and a vane pump drive shaft as a tro
  • a trochoid pump and a vane pump are arranged in parallel with respect to a housing, and a dedicated drive shaft is provided for each.
  • a suction port and a discharge port for the trochoid pump and a suction port and a discharge port for the vane pump are respectively provided in the housing. Therefore, the housing is increased in size, the passages corresponding to the two suction ports and the two discharge ports are complicated, and the cost is increased.
  • Other composite pumps include a housing, a trochoid pump composed of an inner rotor and an outer rotor, a drive shaft of the trochoid pump, an outer rotor of the trochoid pump, and a plurality of guides arranged in a guide groove formed on the outer peripheral surface thereof.
  • a vane pump or the like made of a vane for example, see Patent Document 2.
  • the trochoid pump and the vane pump are driven to rotate by one drive shaft, the inlet and outlet for the trochoid pump and the inlet and outlet for the vane pump are provided to the housing, respectively. Yes. Therefore, the passages corresponding to the two suction ports and the two discharge ports become complicated and costly. Further, in order to allow the vane to slide and perform the pumping action, the inner peripheral surface of the housing that rotatably supports the outer rotor is thinned over 180 degrees to form a pump chamber. Therefore, it is difficult to rotatably support the outer rotor on the inner peripheral surface of the housing, which is not realistic.
  • the length of the illustrated thin plate-like vane is short, and it is difficult to be supported by the guide groove of the outer rotor so that the vane does not rattle in the protruding state, and the reality is poor.
  • the vane if the vane is lengthened and the guide groove is deepened, the vane can be reliably supported, but the outer diameter of the outer rotor is increased, resulting in an increase in the size of the housing.
  • the present invention has been made in view of the above circumstances, and the object of the present invention is to increase the discharge amount or the high pressure type that can increase the discharge pressure by solving the problems of the conventional technology. It is to provide a composite pump.
  • the composite pump of the present invention includes a housing, a first pump unit that is disposed in the housing and includes an inner rotor and an outer rotor, and a first pump unit that is disposed in the housing and includes a plurality of vanes that can be protruded and retracted in the radial direction on the outer periphery of the outer rotor.
  • 2 pump units, and the housing has one suction port through which fluid is sucked toward the first pump unit and the second pump unit, and the fluid pressurized by the first pump unit and the second pump unit. It has the structure which has one discharge outlet discharged.
  • the vane may be a roller vane formed in a columnar shape.
  • the operation of the second pump unit includes a supercharging pump stroke that returns the pressurized fluid sucked from the suction port to the suction port side, and discharges the pressurized fluid sucked from the suction port.
  • a configuration including a main pump stroke that discharges toward the outlet may be adopted.
  • the housing adopts a configuration including a supercharging pump chamber corresponding to the supercharging pump stroke of the second pump unit and a main pump chamber corresponding to the main pumping stroke of the second pump unit. May be.
  • the housing may include a passage that joins the fluid pressurized by the second pump unit to the fluid pressurized by the first pump unit and guides the fluid to the discharge port. Good.
  • the housing has a passage for guiding the fluid pressurized by the first pump unit to the second pump unit, and a passage for guiding the fluid pressurized by the second pump unit to the discharge port.
  • a configuration may be adopted.
  • the housing defines a suction port, a discharge port, and a passage that joins the fluid pressurized by the first pump unit to the fluid pressurized by the second pump unit and leads the fluid to the discharge port.
  • a configuration may be adopted that includes a base that performs rotation, a rotor case that rotatably supports the outer periphery of the outer rotor, and a cover that closes an opening of the rotor case.
  • the housing includes a suction port, a discharge port, a passage for guiding the fluid pressurized by the first pump unit to the second pump unit, and the fluid pressurized by the second pump unit.
  • a configuration may be adopted that includes a base that defines a passage leading to the outer periphery, a rotor case that rotatably supports the outer periphery of the outer rotor, and a cover that closes the opening of the rotor case.
  • a configuration including a drive shaft that is rotatably supported by the housing and connected to the inner rotor may be adopted.
  • the inner rotor and the outer rotor of the first pump unit are composed of trochoidal four leaves and five nodes, and the plurality of vanes of the second pump unit are arranged at equal intervals on the outer periphery of the outer rotor.
  • a configuration consisting of only five vanes may be adopted.
  • the desired pump can be achieved by preventing the occurrence of cavitation and the like while achieving the simplification of structure, size reduction, cost reduction, reduction of driving load by reducing the sliding area, etc. It is possible to obtain an increase type composite pump capable of ensuring performance and increasing the discharge amount or a high pressure type composite pump capable of increasing the discharge pressure.
  • FIG. 1 is an external perspective view showing a first embodiment of a composite pump according to the present invention. It is a disassembled perspective view of the composite pump shown in FIG.
  • FIG. 3 is a schematic diagram of the composite pump (increase type composite pump) shown in FIGS. 1 and 2.
  • FIG. 3 is a front view showing the inside of the composite pump shown in FIGS. 1 and 2 (an inner rotor, an outer rotor, a plurality of roller vanes, a base of a housing, and a rotor case).
  • FIG. 3 is a front view showing a base and a rotor case of a housing included in the composite pump shown in FIGS. 1 and 2.
  • FIG. 3 is an operation diagram at a predetermined rotational position in order to explain the operation of the composite pump (increasing type composite pump) shown in FIGS. 1 and 2.
  • FIG. 6B is an operation diagram at a position rotated by a predetermined angle from the position shown in FIG. 6A in order to explain the operation of the composite pump (increasing type composite pump) shown in FIGS. 1 and 2.
  • FIG. 6 is an operation diagram at a position rotated by a predetermined angle from the position shown in FIG. 6B in order to explain the operation of the composite pump (increasing type composite pump) shown in FIGS. 1 and 2.
  • FIG. 7B is an operation diagram at a position rotated by a predetermined angle from the position shown in FIG.
  • FIG. 7 is an operation diagram at a position rotated by a predetermined angle from the position shown in FIG. 7B in order to explain the operation of the composite pump (increasing type composite pump) shown in FIGS. 1 and 2.
  • FIG. 8B is an operation diagram at a position rotated by a predetermined angle from the position shown in FIG. 8A in order to explain the operation of the composite pump (increasing type composite pump) shown in FIGS. 1 and 2.
  • FIG. 9 is an operation diagram at a position rotated by a predetermined angle from the position shown in FIG.
  • FIG. 9B is an operation diagram at a position rotated by a predetermined angle from the position shown in FIG. 9A in order to explain the operation of the composite pump (increasing type composite pump) shown in FIGS. 1 and 2.
  • It is a graph which shows the discharge characteristic of the 1st pump unit (trochoid pump) and the 2nd pump unit (roller vane pump) in the composite pump (intensification type composite pump) shown in FIG.1 and FIG.2.
  • It is a schematic diagram which shows 2nd Embodiment (high pressure type composite pump) of the composite pump which concerns on this invention.
  • FIG. 9B is an operation diagram at a position rotated by a predetermined angle from the position shown in FIG. 9A in order to explain the operation of the composite pump (increasing type composite pump) shown in FIGS. 1 and 2.
  • It is a graph which shows the discharge characteristic of the 1st pump unit (trochoid pump) and the 2nd pump unit (roller vane pump) in the composite
  • FIG. 12 is a front view showing the inside of the composite pump shown in FIG. 11 (an inner rotor, an outer rotor, a plurality of roller vanes, a base of a housing, and a rotor case). It is a front view which shows the base and rotor case of the housing which are contained in the composite pump shown in FIG.
  • FIG. 14 is a view showing a suction port, a discharge port, and a passage formed in the housing (base and rotor case) shown in FIG. 13, and is a cross-sectional view taken along line E1-E1 in FIG.
  • FIG. 14 shows a suction port, a discharge port, and a passage formed in the housing (base and rotor case) shown in FIG.
  • FIG. 13 is an operation diagram at a predetermined rotational position for explaining the operation of the composite pump (high-pressure composite pump) shown in FIGS. 11 and 12.
  • FIG. 15 is an operation diagram at a position rotated by a predetermined angle from the position shown in FIG. 15A in order to explain the operation of the composite pump (high-pressure type composite pump) shown in FIGS. 11 and 12.
  • FIG. 15 is an operation diagram at a position rotated by a predetermined angle from the position shown in FIG. 15B in order to explain the operation of the composite pump (high-pressure type composite pump) shown in FIGS. 11 and 12.
  • FIG. 16 is an operation diagram at a position rotated by a predetermined angle from the position shown in FIG.
  • FIG. 16 is an operation diagram at a position rotated by a predetermined angle from the position shown in FIG. 16B in order to explain the operation of the composite pump (high-pressure type composite pump) shown in FIGS. 11 and 12.
  • FIG. 19 is an operation diagram at a position rotated by a predetermined angle from the position shown in FIG. 17A in order to explain the operation of the composite pump (high-pressure type composite pump) shown in FIGS. 11 and 12.
  • FIG. 19 is an operation diagram at a position rotated by a predetermined angle from the position shown in FIG. 17B in order to explain the operation of the composite pump (high-pressure type composite pump) shown in FIGS. 11 and 12.
  • FIG. 19 is an operation diagram at a position rotated by a predetermined angle from the position shown in FIG. 18A in order to explain the operation of the composite pump (high-pressure type composite pump) shown in FIGS. 11 and 12. It is a schematic diagram which shows the modification of the composite pump (increase type composite pump) shown in FIG. It is a schematic diagram which shows the modification of the composite pump (high pressure type composite pump) shown in FIG.
  • the composite pump M1 is an increase type pump that pressurizes and supplies oil as a fluid in a lubrication system of an application object such as an engine or a transmission.
  • the composite pump M1 includes a housing H composed of a base 10, a rotor case 20, and a cover 30, a drive shaft 40 that rotates in the direction of arrow R (counterclockwise in FIG. 4) around a center line L1, an inner rotor 50, An outer rotor 60 and a plurality of vanes 70 are provided.
  • the inner rotor 50 and the outer rotor 60 constitute a first pump unit PU1.
  • the outer rotor 60 and the plurality of vanes 70 constitute a second pump unit PU2.
  • the composite pump M1 joins the oil pressurized by the first pump unit PU1 and the oil pressurized by the second pump unit PU2 through the oil pan OP and the passage of the object to be applied. Then, it discharges toward the lubrication area of the object to be applied.
  • the base 10 is formed in a flat plate shape that defines a joining surface 10a joined to the application target and a joining surface 10b joined to the rotor case 20 using a material such as steel, cast iron, sintered steel, and aluminum alloy. ing.
  • the base 10 is fastened to a bearing hole 11, a suction port 12, passages 12a, 12b, 12c communicating with the suction port 12, a discharge port 13, a passage 13a communicating with the discharge port 13, two positioning holes 14, and an object to be applied.
  • the bearing hole 11 is formed so as to rotatably support the drive shaft 40 around the center line L1.
  • the suction port 12 has a substantially crescent-shaped outline indicated by a two-dot chain line, and is formed so as to penetrate from the joint surface 10a to the joint surface 10b.
  • the suction port 12 corresponds to the oil supply port of the object to be applied, and the oil is directly sucked from the oil supply port toward the first pump unit PU1, and the second pump unit PU2 passes through the passages 12a and 12c. It is formed as a single suction port that is shared so that the oil can be sucked toward the vehicle.
  • the passages 12a, 12b, and 12c are formed so as to penetrate from the joint surface 10a to the joint surface 10b, similarly to the suction port 12.
  • the passage 12a is formed to guide oil from the suction port 12 to the supercharging pump chamber C1 of the second pump unit PU2.
  • the passage 12b is formed so as to guide the oil pressurized in the supercharging pump chamber C1 of the second pump unit PU2 back to the suction port 12 again.
  • the passage 12c is formed so as to guide oil from the suction port 12 to the main pump chamber C2 of the second pump unit PU2.
  • the passages 12a, 12b, and 12c are configured such that the opening on the joint surface 10a side is closed by the joint surface of the application object in a state where the composite pump M1 is attached to the application object.
  • the passages 12a, 12b, and 12c are formed so as to communicate with and penetrate the suction port 12. Therefore, when cutting, the processing work is facilitated, and when molding is performed using a mold. The die cutting becomes easy.
  • the passages 12a, 12b, and 12c may be formed in a groove shape that does not penetrate the joint surface 10a instead of the through passage as described above.
  • the discharge port 13 has a substantially crescent shaped outline indicated by a two-dot chain line, and is formed so as to penetrate from the joint surface 10a to the joint surface 10b.
  • the discharge port 13 corresponds to the oil introduction port of the object to be applied, and the oil pressurized by the first pump unit PU1 and the oil pressurized by the second pump unit PU2 and passed through the passage 13a are merged and discharged. Therefore, it is formed as one discharge port that is shared.
  • the passage 13a is formed so as to penetrate from the joint surface 10a to the joint surface 10b.
  • the passage 13a is formed to guide oil pressurized in the main pump chamber C2 of the second pump unit PU2 to the discharge port 13.
  • the passage 13a is configured such that the opening on the joint surface 10a side is closed by the joint surface of the application object in a state where the composite pump M1 is attached to the application object. In this way, the passage 13a is formed so as to communicate with and penetrate the discharge port 13, so that the machining operation is facilitated when cutting, and the die removal is performed when molding with a mold. It becomes easy.
  • path 13a may be formed in the groove shape which does not penetrate to the joint surface 10a side instead of a through-passage as mentioned above.
  • the base 10 is provided with one suction port 12 and one discharge port 13 shared by the first pump unit PU1 and the second pump unit PU2. Therefore, a simple passage configuration can be achieved, and the simplification, size reduction, cost reduction, and the like of the structure can be achieved.
  • a simple passage configuration can also be achieved in an application object such as an engine or a transmission to which the composite pump M1 is applied.
  • the rotor case 20 is formed in a substantially annular shape that defines a joining surface 20a joined to the joining surface 10b of the base 10 and a joining surface 20b joined to the cover 30 using a material such as steel, cast iron, and sintered steel. ing.
  • the rotor case 20 has two inner wall surfaces 21 and two lightening surfaces 22 and 23 formed on the inner peripheral surface, a fitting hole for fitting the positioning pin D, and a screw hole for screwing the screw B on the same axis. Two formed screw and positioning holes 24 and four circular holes 25 through which fastening bolts pass are provided.
  • the two inner wall surfaces 21 have a curvature of the center line L2 so as to rotatably support the outer peripheral surface 61 of the outer rotor 60 about the center line L2 deviated from the center line L1 by a predetermined amount. It is formed as a circular arc surface having the center of the radius and facing each other across the center line L2. As shown in FIG. 5, the two lightening surfaces 22, 23 are not in contact with the outer peripheral surface 61 of the outer rotor 60 and are substantially in cooperation with the outer peripheral surface 61 in a region deviated from the two inner wall surfaces 21. It is formed so as to define a space having a crescent-shaped outline.
  • the supercharging pump chamber C1 of the second pump unit PU2 is defined by the lightening surface 22 and the outer peripheral surface 61.
  • the main pump chamber C2 of the second pump unit PU2 is defined by the lightening surface 23 and the outer peripheral surface 61.
  • the supercharging pump chamber C1 and the main pump chamber C2 are formed in regions facing each other across the rotation center (center line L2) of the outer rotor 60. Therefore, the outer rotor 60 can be supported so as to be sandwiched from both sides in the radial direction by the two inner wall surfaces 21 located in a region excluding the regions of the supercharging pump chamber C1 and the main pump chamber C2. Particularly, since the outer rotor 60 is supported over a half circumference (180 degrees) or more, the outer rotor 60 can be reliably supported in a freely rotatable manner.
  • the cover 30 is made of a material such as steel, cast iron, sintered steel, aluminum alloy or the like, and is formed into a flat plate shape that defines a joint surface 30a that is joined to the joint surface 20b of the rotor case 20 and closes the opening of the rotor case 20. Is formed.
  • the cover 30 includes two circular holes 31 through which the screws B are passed, and four circular holes 32 through which the fastening bolts are passed.
  • the housing H is configured by the base 10, the rotor case 20, and the cover 30, and the suction port 12, the discharge port 13, and the passages 12a, 12b, 12c, and 13a are provided to the base 10, so that the rotor The case 20 and the cover 30 can have a simple structure. Further, in the relationship with the application object to which the composite pump M1 is applied, only the relationship between the suction port 12 and the discharge port 13 of the base 10 need be considered. Furthermore, by simply changing the base 10, not only the increase type composite pump M1 but also the high pressure type composite pump can be easily set while sharing other components.
  • the drive shaft 40 is formed to extend in the direction of the center line L1 using steel or the like.
  • the drive shaft 40 is provided in the coupling portion 41 that transmits the driving force from the application target, the fitting portion 42 that is fitted in the fitting hole 51 of the inner rotor 50, and the rotation prevention pin E provided in the fitting portion 42.
  • a through-hole 43 to be fitted is provided.
  • the drive shaft 40 is rotatably supported by the housing H (base 10) and is connected to the inner rotor 50.
  • the drive shaft 40 is also incorporated as a component, so that the number of handling parts can be reduced, and a drive shaft according to the application object can be appropriately incorporated, corresponding to various application objects. be able to.
  • the inner rotor 50 is formed using a material such as steel or sintered steel into a substantially star shape that defines an end surface 50 a that slides on the joint surface 10 b of the base 10 and an end surface 50 b that slides on the joint surface 30 a of the cover 30.
  • the inner rotor 50 is formed as an external gear having a tooth shape with a trochoidal curve, which includes a fitting hole 51, a pin groove 52, four convex portions (ridges) 53, and four concave portions (valleys) 54.
  • the fitting hole 51 is formed so that the fitting portion 42 of the drive shaft 40 is fitted.
  • the pin groove 52 is formed so as to fit both side portions of the rotation stopper pin E inserted into the through hole 43 of the drive shaft 40. Then, the inner rotor 50 rotates counterclockwise in FIG. 4 around the center line L1 by the drive shaft 40.
  • the outer rotor 60 is formed in an annular shape that defines an end surface 60a that slides on the joint surface 10b of the base 10 and an end surface 60b that slides on the joint surface 30a of the cover 30 using a material such as steel or sintered steel. ing.
  • the outer rotor 60 includes a circular outer peripheral surface 61 centered on the center line L2, and a plurality (here, five) guide grooves 62, five convex portions 63, and five concave portions 64 provided on the outer peripheral surface 61. Further, it is formed as an internal gear having a tooth shape that can mesh with the inner rotor 50.
  • the outer peripheral surface 61 is formed so as to contact the inner wall surface 21 of the rotor case 20 and be rotatably supported.
  • the five guide grooves 62 are formed at regular intervals (intervals of about 72 degrees) in the circumferential direction.
  • Each guide groove 62 is formed to extend outward in the radial direction passing through the center line L ⁇ b> 2 and open at the outer peripheral surface 61 in a region corresponding to the convex portion 63.
  • Each guide groove 62 is configured to guide the vane 70 so that the vane 70 can protrude and retract in the radial direction of the outer rotor 60.
  • a passage through which oil passes is partially provided in the side wall of the guide groove 62, and the back of the vane 70 in the guide groove 62 is provided. May not be a negative pressure.
  • the five convex portions 63 and the five concave portions 64 are formed so as to partially mesh with the four convex portions 53 and the four concave portions 54 of the inner rotor 50.
  • the outer rotor 60 rotates counterclockwise in FIG. 4 with the center line L2 as the rotation center at a slower speed than the inner rotor 50 while interlocking with the rotation of the inner rotor 50 rotating about the center line L1. Rotate. Further, when the inner rotor 50 and the outer rotor 60 are partially engaged with each other, a continuously changing pump chamber C is defined between them.
  • the inner rotor 50 and the outer rotor 60 constitute a four-leaf five-section trochoid pump as the first pump unit PU1 that sucks and pressurizes oil into the pump chamber C from the suction port 12 and discharges the oil to the discharge port 13. ing.
  • the vane 70 is formed as a cylindrical roller vane using a material such as steel or sintered steel.
  • the vane 70 is fitted into the guide groove 62 of the outer rotor 60 so as to be able to protrude and retract in the radial direction passing through the center line L ⁇ b> 2.
  • the peripheral surface (the inner wall surface 21 and the lightening surfaces 22, 23) moves while rolling or sliding.
  • the guide groove 62 for guiding the vane 70 so as to be able to appear and retract can be set shallow. Therefore, the backlash of the vane 70 can be prevented without increasing the outer diameter of the outer rotor 60, that is, without causing an increase in size, and the expected function can be ensured.
  • the outer rotor 60 and the plurality of vanes 70 constitute a roller vane pump as a second pump unit PU2 having a supercharging pump stroke and a main pump stroke. That is, in the second pump unit PU2, first, a supercharging pump stroke is performed in which oil is sucked from the suction port 12 through the passage 12a, guided to the supercharging pump chamber C1, pressurized, and returned to the suction port 12 through the passage 12c. Done. Thereafter, a main pump stroke is performed in which oil is sucked from the suction port 12 through the passage 12c, led to the main pump chamber C2 and pressurized, and discharged to the discharge port 13 through the passage 13a.
  • the second pump unit PU2 also uses the outer rotor 60 of the first pump unit PU1 as a functional part of the pump. Therefore, as a whole, reduction of the number of parts, narrowing, downsizing, reduction of frictional resistance by reduction of sliding area, reduction of driving load, and the like can be achieved.
  • the base 10 the rotor case 20, the cover 30, the drive shaft 40, the inner rotor 50, the outer rotor 60, the five vanes 70, the two screws B, the two positioning pins D, and the one detent pin E are prepared.
  • the rotor case 20 is joined to the base 10 while the positioning pins D are press-fitted into the positioning holes 14 and the screw / positioning holes 24 (fitting holes thereof).
  • the inner rotor 50 and the outer rotor 60 are fitted inside the rotor case 20, and the five vanes 70 are fitted into the guide grooves 62 of the outer rotor 60.
  • the rotation prevention pin E is inserted into the through hole 43 of the drive shaft 40, and the fitting portion 42 is fitted into the fitting hole 51 while the drive shaft 40 is passed through the fitting hole 51 and the bearing hole 11.
  • the stop pin E is fitted into the pin groove 52.
  • the drive shaft 40 is rotated integrally with the inner rotor 50.
  • the connection part 41 of the drive shaft 40 is larger than a shaft diameter, the procedure in which the drive shaft 40 is inserted from the joint surface 10a side of the base 10 and then the detent pin E is inserted may be used.
  • the cover 30 is joined to the joint surface 20b of the rotor case 20, and the two screws B are screwed into the screw / positioning holes 24 (screw holes thereof).
  • work at the time of handling the composite pump M1 as a product can be performed easily.
  • the fastening operation is completed by screwing the fastening bolt through the circular holes 32, 25 and 15 and screwing the fastening bolt into the screw hole of the object to be applied.
  • the composite pump M1 is an increase type composite pump in which the pump operation by the first pump unit PU1 and the pump operation by the second pump unit PU2 are performed in parallel.
  • the second pump unit PU2 will be described by paying attention to the front side and the rear side in the rotation direction of one vane 70 (with a black circle mark).
  • 6A on the rear side of the vane 70, oil starts to be sucked into the supercharging pump chamber C1 from the suction port 12 through the passage 12a, and on the front side of the vane 70, the oil enters the supercharging pump chamber C1 in advance.
  • the sucked oil starts to be returned to the suction port 12 through the passage 12b while being pressurized. Subsequently, when the drive shaft 40 rotates by a predetermined angle through the intermediate state shown in FIG.
  • the first pump unit PU1 will be described by paying attention to the front side and the rear side in the rotation direction of one convex portion 53 (with a black circle mark).
  • the drive shaft 40 rotates by a predetermined angle through the inoperative state (no pump operation) shown in FIG. 6A, immediately after the convex portion 53 starts to suck oil from the inlet 12 at the position shown in FIG. 6B. In this state, the oil is sucked into the pump chamber C from the suction port 12 on the front side of the convex portion 53.
  • the discharge timing of the first pump unit PU1 and the discharge timing of the second pump unit PU2 as shown in FIG.
  • the other phase is set to be different from the other by 90 degrees. According to this, since the second pump unit PU2 is set to discharge in a region where the first pump unit PU1 does not discharge or a region where the discharge amount decreases, the discharge pulsation can be reduced, and the smoothed and stable discharge The quantity can be obtained.
  • the second pump unit PU2 performs the supercharging pump stroke. Therefore, as the second pump unit PU2, a wet state with oil is secured in advance by the supercharging pump stroke, and a smooth pumping action can be obtained in the main pump stroke. In addition, as the first pump unit PU1, the oil pressure is increased by the amount that is supercharged at the time of inhalation, and the occurrence of cavitation and the like can be prevented.
  • cavitation or the like is generated while achieving simplification of the structure, size reduction, cost reduction, reduction of driving load by reducing a sliding region, and the like.
  • the composite pump M2 is a high-pressure pump that supplies oil as a fluid with multistage pressurization in a lubrication system of an application target such as an engine or a transmission.
  • symbol is attached
  • the composite pump M2 includes a housing H ′ composed of a base 10 ′, a rotor case 20 ′, and a cover 30 ′, a drive shaft 40, an inner rotor 50, an outer rotor 60, A plurality of vanes 70 are provided.
  • the base 10 ′ is substantially the same as the base 10 except for the form, and includes a bearing hole 11, a suction port 12, passages 12 a and 12 b communicating with the suction port 12, a discharge port 13 ′, two positioning holes 14, Four circular holes 15 and a substantially L-shaped passage 16 'are provided.
  • the discharge port 13 ′ has a long outline and is formed so as to penetrate from the joint surface 10a to the joint surface 10b.
  • the discharge port 13 ′ corresponds to the oil introduction port of the object to be applied, and serves as one discharge port that discharges the oil pressurized in multiple stages by the first pump unit PU1 and the second pump unit PU2 through the passage 26 ′. Is formed.
  • the passage 16 ′ has a substantially L-shaped groove shape in which the joint surface 10 b side of the base 10 ′ is thinned to a predetermined depth, and the oil pressurized in the pump chamber C of the first pump unit PU 1 It is formed to lead to the main pump chamber C2 of the pump unit PU2.
  • the rotor case 20 ′ is substantially the same as the rotor case 20 except for the form, and includes two inner wall surfaces 21, two lightening surfaces 22 and 23, two screws and positioning holes 24, and four circular holes 25. , A passage 26 'is provided.
  • the passage 26 ′ is formed by partially thinning the oil so that oil pressurized in the main pump chamber C 2 of the second pump unit PU 2 is guided to the discharge port 13 ′.
  • the cover 30 ′ is substantially the same as the cover 30 except for the form, and includes two circular holes 31, four circular holes 32, and the like.
  • the composite pump M2 guides the oil pressurized by the first pump unit PU1 to the second pump unit PU2 through the oil pan OP and the passage of the application target, and the second pump unit PU2 Then, the further pressurized oil is discharged toward the lubrication region of the object to be applied.
  • the composite pump M2 is a high-pressure composite pump in which the pump operation by the first pump unit PU1 and the pump operation by the second pump unit PU2 are performed in series to perform multistage pressurization.
  • the rear side of the vane 70 is in a state immediately before oil starts to be sucked into the supercharging pump chamber C1 from the suction port 12 through the passage 12a, and the supercharging is performed in advance on the front side of the vane 70.
  • the oil just sucked into the pump chamber C1 is in a state immediately before being started to be returned to the suction port 12 through the passage 12b while being pressurized.
  • the convex part 53 exists in the state of non-operation (no pump operation
  • the vane 70 is in an inoperative state at the position shown in FIG. 17A. Further, the oil is sucked into the pump chamber C from the suction port 12 on the rear side of the convex portion 53, and the oil in the pump chamber C is discharged toward the passage 16 'on the front side of the convex portion 53. In the middle of being.
  • the vane 70 is in an inoperative state at the position shown in FIG. 17B. Further, at the rear side of the convex portion 53, the oil suction operation from the suction port 12 into the pump chamber C is completed, and at the same time, the oil is discharged toward the passage 16 '. Then, the oil in the pump chamber C is in the middle of being guided into the main pump chamber C2 through the passage 16 '.
  • the second pump unit PU2 performs the supercharging pump stroke. Therefore, as the second pump unit PU2, a wet state with oil is secured in advance by the supercharging pump stroke, and a smooth pumping action can be obtained in the main pump stroke. In addition, as the first pump unit PU1, the oil pressure is increased by the amount that is supercharged at the time of inhalation, and the occurrence of cavitation and the like can be prevented.
  • cavitation or the like is generated while achieving simplification of the structure, size reduction, cost reduction, reduction of the driving load by reducing the sliding area, and the like.
  • 2nd pump unit PU2 contains a supercharging pump stroke.
  • the present invention is not limited to this, and when the initial suction performance in the vane pump or the like is ensured and the cavitation in the trochoid pump or the like is eliminated, the supercharging pump stroke (passages 12a and 12b) is abolished.
  • the second pump unit PU2 ′ can also be employed. And as shown in FIG. 19, you may employ
  • the present invention is not limited to this, and the present invention may be applied to a configuration including an inner rotor and an outer rotor having an involute tooth profile, or an inner rotor and an outer rotor having other tooth profiles.
  • the inner rotor 50 and the outer rotor 60 are composed of trochoidal four-leaf five-nodes, and the plurality of vanes 70 are composed of five vanes.
  • the present invention is not limited to this. You may employ
  • the configuration including the drive shaft 40 is shown as the composite pumps M1 and M2, but the present invention is not limited to this.
  • the composite pump may be configured without the drive shaft.
  • the present invention is not limited to this, and is applied to other lubrication systems.
  • the present invention may be applied to an apparatus using a fluid other than oil.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)

Abstract

La présente invention concerne une pompe composite qui comporte : un boîtier (H) ; une première unité de pompe (PU1) disposée dans le boîtier et comprenant un rotor interne (50) et un rotor externe (60), qui viennent en prise l'un avec l'autre ; et une deuxième unité de pompe (PU2) disposée dans le boîtier et comprenant une pluralité d'aubes (70) pouvant être déployées et rétractées radialement à la périphérie externe du rotor externe. Le boîtier (H) comporte : une ouverture d'aspiration unique (12) dans laquelle un fluide est aspiré vers la première unité de pompe (PU1) et la deuxième unité de pompe (PU2) ; et une ouverture de décharge unique (13) depuis laquelle le fluide mis sous pression par la première unité de pompe (PU1) et la deuxième unité de pompe (PU2) est évacué. Grâce à cette configuration, une simplification de structure, une réduction de taille, une réduction de coût, une réduction de charge d'entraînement, etc., peuvent être obtenues.
PCT/JP2017/014433 2016-04-27 2017-04-07 Pompe composite Ceased WO2017187928A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2016-089615 2016-04-27
JP2016089615A JP6745132B2 (ja) 2016-04-27 2016-04-27 複合ポンプ

Publications (1)

Publication Number Publication Date
WO2017187928A1 true WO2017187928A1 (fr) 2017-11-02

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Application Number Title Priority Date Filing Date
PCT/JP2017/014433 Ceased WO2017187928A1 (fr) 2016-04-27 2017-04-07 Pompe composite

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JP (1) JP6745132B2 (fr)
WO (1) WO2017187928A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102023122127A1 (de) * 2023-07-06 2025-01-09 Thomas Magnete Gmbh Gerotorpumpe und Motor-Pumpen-Einheit

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102019201864B4 (de) * 2019-02-13 2021-07-22 Hanon Systems Efp Deutschland Gmbh Kühl-Schmiersystem mit Trockensumpf

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS4939805A (fr) * 1972-08-23 1974-04-13
JPS49103034A (fr) * 1973-01-22 1974-09-28
JPS6380085A (ja) * 1985-08-20 1988-04-11 Yoshio Ono 吐流反作用吸収形ポンプ
JP2002285813A (ja) * 2001-03-27 2002-10-03 Toyoda Spinning & Weaving Co Ltd 内燃機関用オイルポンプ及びその使用方法
JP2005133716A (ja) * 2003-10-10 2005-05-26 Borgwarner Inc 可変目標調整器を備えた可変容量形ベーンポンプ
JP2009275537A (ja) * 2008-05-13 2009-11-26 Kayaba Ind Co Ltd 可変容量型ベーンポンプ
JP2010158975A (ja) * 2009-01-08 2010-07-22 Jtekt Corp 油圧供給装置

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS4939805A (fr) * 1972-08-23 1974-04-13
JPS49103034A (fr) * 1973-01-22 1974-09-28
JPS6380085A (ja) * 1985-08-20 1988-04-11 Yoshio Ono 吐流反作用吸収形ポンプ
JP2002285813A (ja) * 2001-03-27 2002-10-03 Toyoda Spinning & Weaving Co Ltd 内燃機関用オイルポンプ及びその使用方法
JP2005133716A (ja) * 2003-10-10 2005-05-26 Borgwarner Inc 可変目標調整器を備えた可変容量形ベーンポンプ
JP2009275537A (ja) * 2008-05-13 2009-11-26 Kayaba Ind Co Ltd 可変容量型ベーンポンプ
JP2010158975A (ja) * 2009-01-08 2010-07-22 Jtekt Corp 油圧供給装置

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102023122127A1 (de) * 2023-07-06 2025-01-09 Thomas Magnete Gmbh Gerotorpumpe und Motor-Pumpen-Einheit

Also Published As

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JP6745132B2 (ja) 2020-08-26
JP2017198144A (ja) 2017-11-02

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