WO2017187928A1

WO2017187928A1 - Compound pump

Info

Publication number: WO2017187928A1
Application number: PCT/JP2017/014433
Authority: WO
Inventors: 竹花　憲夫
Original assignee: 株式会社ミクニ
Priority date: 2016-04-27
Filing date: 2017-04-07
Publication date: 2017-11-02
Also published as: JP2017198144A; JP6745132B2

Abstract

This compound pump is provided with: a housing (H); a first pump unit (PU1) disposed within the housing and including an inner rotor (50) and an outer rotor (60), which engage with each other; and a second pump unit (PU2) disposed within the housing and including a plurality of vanes (70) capable of radially protruding and retracting at the outer periphery of the outer rotor. The housing (H) has: a single suction opening (12) into which fluid is sucked toward the first pump unit (PU1) and the second pump unit (PU2); and a single discharge opening (13) from which the fluid pressurized by the first pump unit (PU1) and the second pump unit (PU2) is discharged. As a result of this configuration, a simplification in structure, a reduction in size, a reduction in cost, a reduction in a drive load, etc. can be achieved.

Description

Compound pump

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. One having two gears or the like to be interlocked is known (for example, see Patent Document 1).

In this composite pump, 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. In addition, 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. There is known one provided with a vane pump or the like made of a vane (for example, see Patent Document 2).

In this composite pump, although 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.

Furthermore, 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. On the other hand, 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.

Japanese Patent Laid-Open No. 2003-27912 JP-A-63-80085

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.

In the composite pump having the above configuration, the vane may be a roller vane formed in a columnar shape.

In the composite pump configured as described above, 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.

In the composite pump configured as described above, 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.

In the composite pump configured as described above, a configuration in which the supercharging pump chamber and the main pump chamber are formed in regions facing each other across the rotation center of the outer rotor may be adopted.

In the composite pump having the above-described configuration, 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.

In the composite pump having the above configuration, a configuration in which the discharge timing of the second pump unit is set to a phase different from the discharge timing of the first pump unit may be adopted.

In the composite pump configured as described above, 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.

In the composite pump configured as described above, 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.

In the composite pump configured as described above, 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.

In the composite pump having the above-described configuration, a configuration including a drive shaft that is rotatably supported by the housing and connected to the inner rotor may be adopted.

In the composite pump configured as described above, 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.

According to the composite pump having the above-described configuration, 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.

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. 7A in order to explain the operation of the composite pump (increasing type composite pump) shown in FIGS. 1 and 2. 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. 8B in order to explain the operation of the composite pump (increasing type composite pump) shown in FIGS. 1 and 2. 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. 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. 13, and is a partial sectional view taken along line E2-E2 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. 16A 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. 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.

Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings.
As shown in FIGS. 1 to 10, the composite pump M1 according to the first embodiment 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.

Here, 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.
Then, as shown in FIG. 3, 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. There are four circular holes 15 through which fastening bolts (not shown) are passed.

The bearing hole 11 is formed so as to rotatably support the drive shaft 40 around the center line L1.
As shown in FIG. 5, 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.
As described above, 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.
Note that 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.

As shown in FIG. 5, 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.

Similarly to the discharge port 13, 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. In addition, the channel | 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.
As described 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. In addition, 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.

As shown in FIG. 5, 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.

That is, in the state where the outer rotor 60 is incorporated in the rotor case 20, the supercharging pump chamber C1 of the second pump unit PU2 is defined by the lightening surface 22 and the outer peripheral surface 61. In addition, the main pump chamber C2 of the second pump unit PU2 is defined by the lightening surface 23 and the outer peripheral surface 61.

Here, 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.

As described above, 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.
As described above, 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. Has been.
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.
In order to make the vane 70 fitted in the guide groove 62 protrude and retract due to the centrifugal force more smoothly, 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.

As described above, by adopting a cylindrical roller vane as the vane 70, 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.
Here, 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 assembly work of the composite pump M1 having the above configuration will be described.
First, 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. .
Subsequently, 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).

Subsequently, 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.
Subsequently, 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.
As a result, the drive shaft 40 is rotated integrally with the inner rotor 50.
In addition, when 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.

Finally, 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).
This completes the assembly of the composite pump.
Thus, since the housing H is comprised by the base 10, the rotor case 20, and the cover 30, the assembly | attachment operation | work at the time of handling the composite pump M1 as a product can be performed easily.
In addition, when attaching this composite pump M1 to an application target object, contact | connecting the joint surface 10a of the base 10 to the joint surface of an application target object, connecting the connection part 41 of the drive shaft 40 to the connection part of an application target object. Let Thereafter, 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.

Next, the operation of the composite pump M1 will be described with reference to FIGS. 6A to 9B. 6A to 9B show operation states for each time series when the drive shaft 40 rotates counterclockwise.
Here, 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.

First, 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. 6B, the operation of sucking oil into the supercharging pump chamber C1 is completed at the rear side of the vane 70 at the position shown in FIG. 7A. In the front side of the vane 70, the return operation from the supercharging pump chamber C1 to the suction port 12 ends (supercharging pump stroke).

Subsequently, when the drive shaft 40 rotates by a predetermined angle through the inoperative state (no pump operation) shown in FIG. 7B, at the position shown in FIG. 8A, on the rear side of the vane 70, from the inlet 12 through the passage 12c. Oil begins to be sucked into the main pump chamber C2, and oil that has been sucked into the main pump chamber C2 in advance is pressurized toward the discharge port 13 through the passage 13a while being pressurized.
Subsequently, when the drive shaft 40 is rotated by a predetermined angle through the intermediate state shown in FIG. 8B, the suction operation into the main pump chamber C2 is completed on the rear side of the vane 70 at the position shown in FIG. 9A. On the front side, the discharge operation from the main pump chamber C2 to the discharge port 13 is completed (main pump stroke).

Subsequently, when the drive shaft 40 rotates through a predetermined angle through the inoperative state (no pump operation) shown in FIG. 9B, the state returns to the state shown in FIG. 6A and the same operation is repeated again.
Here, the description has been made focusing on one vane 70, but in reality, the five vanes 70 each perform the same operation (supercharging pump stroke and main pump stroke).
Therefore, as the second pump unit PU2, the discharge operation is performed five times while the outer rotor 60 makes one rotation as the drive shaft 40 rotates.

Next, 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).
When 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.

Subsequently, when the drive shaft 40 rotates by a predetermined angle through the intermediate state shown in FIG. 7A, oil is sucked into the pump chamber C from the suction port 12 at the rear side of the convex portion 53 at the position shown in FIG. 7B. In the middle state, the front side of the convex portion 53 is in a state immediately before the oil suction operation from the suction port 12 is finished and immediately before the discharge port 13 starts to discharge the oil.

Subsequently, when the drive shaft 40 rotates by a predetermined angle through the intermediate state shown in FIG. 8A, oil is discharged from the pump chamber C toward the discharge port 13 at the front side of the convex portion 53 at the position shown in FIG. 8B. In the midway state, the rear side of the convex portion 53 is in a state immediately before the suction of oil from the suction port 12 is finished and immediately before the discharge port 13 starts to discharge the oil.

Subsequently, when the drive shaft 40 rotates by a predetermined angle through the intermediate state shown in FIG. 9A, the discharge operation from the pump chamber C to the discharge port 13 ends at the front side of the convex portion 53 at the position shown in FIG. 9B.
Subsequently, when the drive shaft 40 rotates by a predetermined angle, the state returns to the state shown in FIG. 6A and the same operation is repeated again.

Here, the description has been made focusing on one convex portion 53, but actually, the four convex portions 53 each perform the same operation (pump stroke).
Accordingly, the first pump unit PU1 performs four discharge operations while the drive shaft 40 makes one rotation.

That is, in the first pump unit PU1 and the second pump unit PU2 that perform the pump operation as described above, as 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.

Further, in the course of the operation shown in FIGS. 6A to 7A, 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.

As described above, according to the composite pump M1 according to the above-described embodiment, 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. Thus, it is possible to obtain an increase type composite pump that can secure desired pump performance and increase the discharge amount.

Next, the composite pump M2 according to the second embodiment will be described with reference to FIGS. 11 to 18B. 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.
In addition, about the structure same as the composite pump M1 which concerns on the above-mentioned embodiment, the same code | symbol is attached | subjected and description is abbreviate | omitted.

As shown in FIGS. 1, 11 to 14B, 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.

Then, as shown in FIG. 11, 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.

Next, the operation of the composite pump M2 will be described with reference to FIGS. 15A to 18B. 15A to 18B show operation states for each time series when the drive shaft 40 rotates counterclockwise.
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.

Here, on the front side and the rear side in the rotation direction of one vane 70 (with black circles) in the second pump unit PU2 and one convex portion 53 (with black circles) in the first pump unit PU1. Focus on the explanation.

In the position shown in FIG. 15A, 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.
Moreover, the convex part 53 exists in the state of non-operation (no pump operation | movement) in the position shown to FIG. 15A.

Subsequently, when the drive shaft 40 rotates by a predetermined angle, at the position shown in FIG. 15B, oil starts to be sucked into the supercharging pump chamber C1 on the rear side of the vane 70, and the supercharging pump precedes the vane 70 on the front side. The oil sucked into the chamber C1 starts to be returned to the suction port 12 through the passage 12b while being pressurized (supercharging pump stroke).
Further, the rear side of the convex portion 53 is in a state immediately before oil starts to be sucked from the suction port 12, and the front side of the convex portion 53 is in a state where oil is sucked into the pump chamber C from the suction port 12. .

Subsequently, when the drive shaft 40 rotates by a predetermined angle, at the position shown in FIG. 16A, the operation of sucking oil into the supercharging pump chamber C1 is completed on the rear side of the vane 70, and the supercharging is performed on the front side of the vane 70. The returning operation from the pump chamber C1 to the suction port 12 ends (supercharging pump stroke).
Further, the rear side and the front side of the convex portion 53 are in a state where oil is sucked into the pump chamber C from the suction port 12.

Subsequently, when the drive shaft 40 rotates by a predetermined angle, the vane 70 is in an inoperative state at the position shown in FIG. 16B. The oil is sucked into the pump chamber C from the suction port 12 on the rear side of the convex portion 53, and at the same time as the oil suction operation into the pump chamber C is completed on the front side of the convex portion 53. A state immediately before the oil is discharged toward the passage 16 'is obtained.

Subsequently, when the drive shaft 40 rotates by a predetermined angle, 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.

Subsequently, when the drive shaft 40 rotates by a predetermined angle, 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 '.

Subsequently, when the drive shaft 40 rotates by a predetermined angle, oil begins to be sucked into the main pump chamber C2 via the passage 16 'on the rear side of the vane 70 at the position shown in FIG. Thus, the oil sucked into the main pump chamber C2 starts to be further discharged and discharged to the discharge port 13 'through the passage 26' (main pump stroke).

Subsequently, when the drive shaft 40 rotates by a predetermined angle, at the position shown in FIG. 18B, the operation of sucking oil into the main pump chamber C2 is completed on the rear side of the vane 70, and the main pump chamber is on the front side of the vane 70. The discharge operation from C2 to the discharge port 13 'ends (main pump stroke).

Here, the description has been made by paying attention to one vane 70 and one convex portion 53, but actually, the five vanes 70 perform the same operation (supercharging pump stroke, main pump stroke), respectively, Each of the convex portions 53 performs the same operation (pump stroke).
Therefore, as the composite pump M2, the discharge operation is performed five times while the outer rotor 60 makes one rotation as the drive shaft 40 rotates.

Further, in the course of the operation shown in FIGS. 15A to 16A, 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.

As described above, according to the composite pump M2 according to the above-described embodiment, 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. Thus, it is possible to obtain a high-pressure composite pump that can secure desired pump performance and increase discharge pressure.

In the said embodiment, it showed about the case where 2nd pump unit PU2 contains a supercharging pump stroke. However, 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 | adopt the increase type composite pump M1 'which employ | adopted 2nd pump unit PU2'.
Further, as shown in FIG. 20, a high-pressure composite pump M2 ′ that employs the second pump unit PU2 ′ may be employed.

In the above embodiment, the case where the present invention is applied to the configuration in which the trochoid pump having the trochoidal tooth profile is adopted as the first pump unit PU1 is shown. However, 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.

In the above embodiment, 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. However, the present invention is not limited to this. You may employ | adopt the structure which consists of these numbers.

In the above embodiment, the case where the present invention is adopted in the configuration in which the housings H and H ′ are separated into the

bases

10 and 10 ′, the

rotor cases

20 and 20 ′, and the

covers

30 and 30 ′ has been described. However, a configuration in which the base and the rotor case are integrated may be employed.

In the above embodiment, 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. For example, if the drive shaft can be assembled after the housing is assembled, the composite pump may be configured without the drive shaft.

In the above-described embodiment, the case where the composite pumps M1 and M2 according to the present invention are applied to an engine or a transmission mounted in an automobile or the like is shown, but the present invention is not limited to this, and is applied to other lubrication systems. Alternatively, the present invention may be applied to an apparatus using a fluid other than oil.

M1, M1 ′, M2, M2 ′ Composite pump PU1 First pump unit PU2, PU2 ′ Second pump unit H, H ′

Housing

10, 10 ′ Base (housing)
12

Inlet

12a, 12b, 12c Passage 13, 13 'Discharge 13a Passage 16' Passage 20, 20 'Rotor case (housing)
26 'passage 30, 30' cover (housing)
40 Drive shaft L1 Center line (Rotation center)
50 Inner rotor (first pump unit)
60 Outer rotor (first pump unit, second pump unit)
L2 center line (center of rotation)
70 vane (roller vane, second pump unit)

Claims

A housing;
A first pump unit including an inner rotor and an outer rotor disposed in the housing and meshing with each other;
A second pump unit including a plurality of vanes arranged in the housing and freely projecting and retracting in a radial direction on an outer periphery of the outer rotor,
The housing has one suction port through which fluid is sucked toward the first pump unit and the second pump unit, and one fluid from which the fluid pressurized by the first pump unit and the second pump unit is discharged. Having a discharge port,
A composite pump characterized by that.
The vane is a roller vane formed in a columnar shape,
The composite pump according to claim 1.
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 the fluid sucked and pressurized from the suction port toward the discharge port. Including a main pump stroke to be discharged
The composite pump according to claim 1 or 2, characterized in that.
The housing includes a supercharging pump chamber corresponding to the supercharging pump stroke, and a main pumping chamber corresponding to the main pump stroke.
The composite pump according to claim 3.
The supercharging pump chamber and the main pump chamber are formed in regions facing each other across the rotation center of the outer rotor,
The composite pump according to claim 4.
The housing includes 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.
The composite pump according to any one of claims 1 to 5, wherein
The discharge timing of the second pump unit is set to a phase different from the discharge timing of the first pump unit.
The composite pump according to claim 6.
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.
The composite pump according to any one of claims 1 to 5, wherein
The housing includes a base that defines the suction port, the discharge port, and the passage, a rotor case that rotatably supports an outer periphery of the outer rotor, and a cover that closes an opening of the rotor case. ,
The composite pump according to claim 6.
The housing includes a base that defines the suction port, the discharge port, and the two passages, a rotor case that rotatably supports an outer periphery of the outer rotor, a cover that closes an opening of the rotor case, including,
The composite pump according to claim 8.
Including a drive shaft rotatably supported by the housing and coupled to the inner rotor;
The composite pump according to any one of claims 1 to 10, wherein
The inner rotor and the outer rotor of the first pump unit are composed of trochoidal four leaves and five nodes,
The plurality of vanes of the second pump unit includes five vanes arranged at equal intervals on the outer periphery of the outer rotor.
The composite pump according to claim 1, wherein the composite pump is characterized in that