JP6745132B2 - Compound pump - Google Patents

Description

The present invention relates to a pump that is applied to a lubrication system such as an engine or a transmission and supplies oil for lubrication, and more particularly to a composite pump that has both a trochoid pump and a vane pump.

As a conventional composite pump, a trochoid pump composed of a housing, an inner rotor and an outer rotor, a drive shaft of a trochoid pump, a vane pump including a cam rotor and a plurality of vanes, a drive shaft of a vane pump, and a drive shaft of a vane pump are used as drive shafts of the trochoid pump. A device having two gears that are interlocked with each other is known (see, for example, Patent Document 1).

In this composite pump, a trochoid pump and a vane pump are arranged in parallel with respect to the housing, and a dedicated drive shaft is provided for each. Further, a suction port and a discharge port for the trochoid pump, and a suction port and a discharge port for the vane pump are provided on the housing, respectively.
Therefore, the size of the housing is increased, the passages corresponding to the two suction ports and the two discharge ports are complicated, and the cost is increased.

As another composite pump, a trochoid pump including a housing, 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 retractably arranged guide grooves formed on the outer peripheral surface thereof. There is known one provided with a vane pump or the like composed of vanes (see, for example, Patent Document 2).

In this composite pump, the trochoid pump and the vane pump are rotationally driven by one drive shaft, but the housing is provided with an inlet and an outlet for the trochoid pump, and an inlet and an outlet for the vane pump, respectively. There is. Therefore, the passages corresponding to the two suction ports and the two discharge ports are complicated and the cost is increased.
Further, in order to perform the pumping action by sliding the vane, the inner peripheral surface of the housing that rotatably supports the outer rotor is lightened 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 practical.

Further, the illustrated thin plate-shaped vane has a short length and is difficult to be supported by the guide groove of the outer rotor so as to prevent the vane from rattling in the protruding state, which is not practical. 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 becomes large and the housing becomes large.

JP, 2003-27912, A JP-A-63-80085

The present invention has been made in view of the above circumstances, and an object thereof is to simplify the structure, reduce the size, reduce the cost, reduce the driving load by reducing the sliding area, and the like. It is an object of the present invention to provide a compound pump of an increasing type capable of ensuring desired pump performance and increasing a discharge amount or a high pressure type capable of increasing a discharge pressure by preventing occurrence of cavitation and the like.

A composite pump of the present invention includes a housing, a first pump unit that is disposed inside the housing and includes an inner rotor and an outer rotor, and a plurality of vanes that are disposed inside the housing and that can vane in and out in the radial direction on the outer circumference of the outer rotor. Two pump units are provided, and the housing has one suction port for sucking fluid toward the first pump unit and the second pump unit and a fluid pressurized by the first pump unit and the second pump unit. have a single discharge port to be ejected, the operation of the second pump unit includes a supercharging pump stroke to return the sucked by pressurized fluid from the inlet port to the suction port side, pressurized by suction from the suction port The housing includes a main pump stroke for discharging the fluid toward the discharge port, and the housing includes a supercharging pump chamber corresponding to the supercharging pump stroke and a main pump chamber corresponding to the main pump stroke .

According to this configuration, when the fluid passages of the first pump unit and the second pump unit (vane pump) are connected in parallel, it is possible to obtain an increased volume pump with an increased discharge amount. Moreover, when the fluid passages of the first pump unit and the second pump unit are connected in series, it is possible to obtain a high-pressure type pump whose discharge pressure is increased by multi-stage pressurization.
The second pump unit (vane pump) also uses the outer rotor of the first pump unit as a functional component of the pump. Therefore, as a whole, reduction of the number of parts, narrowing of the width in the direction of the rotation axis, downsizing, reduction of frictional resistance due to reduction of sliding area, reduction of driving load, etc. can be achieved.
Further, the housing is provided with one suction port and one discharge port shared by the first pump unit and the second pump unit. Therefore, the passage structure can be simplified, and the structure can be simplified, the size can be reduced, and the cost can be reduced. Further, even in an object to be applied such as an engine and a transmission to which the composite pump is applied, the passage structure can be made simple.
Here, the operation of the second pump unit is as follows: a supercharging pump stroke in which the fluid sucked from the suction port and pressurized is returned to the suction port side, and the fluid sucked from the suction port and pressurized is discharged toward the discharge port. Since the second pump unit includes the main pump stroke, the second pump unit can secure a wet state with the fluid in advance by the supercharging pump stroke, and can obtain a smooth pumping action in the main pump stroke.
Further, since the fluid pressurized by the supercharging pump stroke is returned to the suction port side again, when the first pump unit starts the suction operation, the fluid pressure is increased by the supercharging amount. Therefore, in particular, it is possible to prevent the occurrence of cavitation or the like on the suction side of the first pump unit.
Particularly, since the housing includes the supercharging pump chamber corresponding to the supercharging pump stroke of the second pump unit and the main pump chamber corresponding to the main pump stroke of the second pump unit, the vane is rotated as the outer rotor rotates. When moving in the supercharging pump chamber, fluid is sucked from the suction port and pressurized, is returned toward the suction port side, and the vane moves in the main pump chamber as the outer rotor rotates. At this time, the fluid is sucked from the suction port, pressurized, and discharged toward the discharge port.

In the composite pump having the above configuration, the vane may be a cylindrical roller vane.
According to this structure, since the vane is a cylindrical roller vane rather than a thin plate, it is possible to set a shallow guide groove for guiding the vane so that it can be retracted and retracted. Therefore, rattling of the roller vanes and the like can be prevented without increasing the outer diameter of the outer rotor, that is, without increasing the size of the outer rotor, and the desired function can be guaranteed.

In the composite pump having the above configuration, the supercharging pump chamber and the main pump chamber may be formed in regions facing each other with the rotation center of the outer rotor interposed therebetween.
According to this structure, the outer rotor can be supported so as to be sandwiched from both sides in the radial direction by the inner wall surface of the other region of the housing excluding the regions of the supercharging pump chamber and the main pump chamber. In particular, since the outer rotor can be supported over a half circumference (180 degrees) or more, the outer rotor can be rotatably and reliably supported.

In the composite pump having the above-mentioned configuration, the housing may have a passage having a passage for combining the fluid pressurized by the first pump unit with the fluid pressurized by the second pump unit and guiding the fluid to the discharge port. Good.
According to this structure, it is possible to obtain an increase-type pump in which the discharge amount of the first pump unit and the discharge amount of the second pump unit (vane pump) are combined only by providing the passage as described above in the housing.

In the composite pump having the above configuration, the discharge timing of the second pump unit may be set to a phase different from the discharge timing of the first pump unit.
According to this configuration, for example, by causing the second pump unit to discharge in a region where the first pump unit does not discharge or a region where the discharge amount decreases, the discharge pulsation can be reduced and a smoothed and stable discharge amount can be obtained. Can be obtained.

In the composite pump having the above configuration, 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.
According to this configuration, by simply providing the above passage in the housing, the fluid pressurized by the first pump unit is further pressurized by the second pump unit and discharged, that is, by the multi-stage pressurization, It is possible to obtain a high-pressure pump having a high discharge pressure.

In the composite pump having the above structure, the housing defines a suction port, a discharge port, and a passage that joins the fluid pressurized by the first pump unit with the fluid pressurized by the second pump unit and guides the fluid to the discharge port. It is also possible to employ a configuration including a base for controlling the outer rotor, a rotor case that rotatably supports the outer circumference of the outer rotor, and a cover that closes the opening of the rotor case.
In addition, the housing defines a suction port, a discharge port, 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 including a base, a rotor case that rotatably supports the outer circumference of the outer rotor, and a cover that closes the opening of the rotor case may be adopted.
According to this configuration, since the suction port, the discharge port, and the passage are provided in the base that configures the housing, other components (the rotor case and the cover) can have a simple structure. In addition, regarding the relationship with the object to which the composite pump is applied, only the relationship between the suction port and the discharge port of the base need be considered. Further, the increase type pump and the high pressure type pump can be easily set only by changing the base while sharing other parts.

The composite pump having the above-described configuration may be configured to include a drive shaft that is rotatably supported by the housing and that is connected to the inner rotor.
According to this configuration, by incorporating the drive shaft as a component, it is possible to reduce the number of parts to be handled, and it is also possible to properly incorporate the drive shaft according to the application target, which corresponds to various application targets. be able to.

In the composite pump having the above configuration, the inner rotor and the outer rotor of the first pump unit are composed of trochoidal four-lobed and five-node, and the plurality of vanes of the second pump unit are arranged at equal intervals on the outer circumference of the outer rotor. Alternatively, a configuration including five vanes may be adopted.
With this configuration, it is possible to obtain a desired increase-type composite pump or a high-pressure type composite pump having a desired discharge pressure while ensuring stable pump performance and durability.

According to the composite pump having the above-described configuration, the cavitation and the like are prevented from occurring while achieving the simplification of the structure, the miniaturization, the cost reduction, the reduction of the driving load by the reduction of the sliding area, and the desired pump. It is possible to obtain an increase type composite pump capable of ensuring the performance and increasing the discharge amount or a high pressure type composite pump capable of increasing the discharge pressure.

It is an appearance perspective view showing one embodiment of the compound pump concerning the present invention. It is a disassembled perspective view of the composite pump shown in FIG. It is a schematic diagram of the composite pump (increasing type composite pump) shown in FIG. 1 and FIG. FIG. 3 is a front view showing the inside (inner rotor, outer rotor, a plurality of roller vanes, the base of the housing, and the rotor case) of the composite pump shown in FIGS. 1 and 2. FIG. 3 is a front view showing a base of a housing and a rotor case included in the composite pump shown in FIGS. 1 and 2. The operation of the composite pump (increase type composite pump) shown in FIGS. 1 and 2 will be described. (a) is an operation diagram at a predetermined rotation position, (b) is a predetermined operation from the position shown in (a) It is an operation view in a position rotated by an angle. The operation of the composite pump (increase type composite pump) shown in FIGS. 1 and 2 is described. FIG. 6A is an operation diagram at a position rotated by a predetermined angle from the position shown in FIG. b) is an operation diagram at a position rotated by a predetermined angle from the position shown in (a). The operation of the composite pump shown in FIG. 1 and FIG. 2 (increase type composite pump) is described, and FIG. 7A is an operation diagram at a position rotated by a predetermined angle from the position shown in FIG. b) is an operation diagram at a position rotated by a predetermined angle from the position shown in (a). The operation of the composite pump shown in FIGS. 1 and 2 (increase type composite pump) will be described. (a) is an operation diagram at a position rotated by a predetermined angle from the position shown in (b) of FIG. b) is an operation diagram at a position rotated by a predetermined angle from the position shown in (a). 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 (increase type composite pump) shown in FIG. 1 and FIG. It is a schematic diagram which shows other embodiment (high-pressure type composite pump) of the composite pump which concerns on this invention. FIG. 12 is a front view showing the inside (inner rotor, outer rotor, a plurality of roller vanes, the base of the housing, and the rotor case) of the composite pump shown in FIG. 11. FIG. 12 is a front view showing a base of a housing and a rotor case included in the composite pump shown in FIG. 11. 13A and 13B show an inlet port, an outlet port, and a passage formed in the housing (base and rotor case) shown in FIG. 13, (a) being a cross-sectional view taken along line E1-E1 in FIG. 13, and (b) being FIG. 7 is a partial cross-sectional view taken along line E2-E2 of FIG. FIGS. 11A and 11B are diagrams for explaining the operation of the composite pump shown in FIGS. 11 and 12 (high-pressure composite pump), in which (a) is an operation diagram at a predetermined rotational position, and (b) is predetermined from the position shown in (a). It is an operation view in a position rotated by an angle. FIG. 13 is a view for explaining the operation of the composite pump (high-pressure composite pump) shown in FIGS. 11 and 12, and FIG. 15A is an operation diagram at a position rotated by a predetermined angle from the position shown in FIG. 15B. b) is an operation diagram at a position rotated by a predetermined angle from the position shown in (a). FIG. 13 is a diagram for explaining the operation of the composite pump (high-pressure composite pump) shown in FIGS. 11 and 12, and FIG. 16A is an operation diagram at a position rotated by a predetermined angle from the position shown in FIG. b) is an operation diagram at a position rotated by a predetermined angle from the position shown in (a). 11A and 11B are diagrams for explaining the operation of the composite pump (high-pressure composite pump) shown in FIGS. 11 and 12, and FIG. 17A is an operation diagram at a position rotated by a predetermined angle from the position shown in FIG. 17B. b) is an operation diagram at a position rotated by a predetermined angle from the position shown in (a). It is a schematic diagram which shows the modification of the composite pump (increasing 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.
The compound pump M1 according to the first embodiment is a volumetric pump that pressurizes and supplies oil as a fluid in a lubrication system of an application target such as an engine and a transmission.
As shown in FIGS. 1 to 5, the compound pump M1 has a housing H composed of a base 10, a rotor case 20 and a cover 30, and a center line L1 as a center of rotation in an arrow R direction (counterclockwise in FIG. 4). It includes a rotating drive shaft 40, an inner rotor 50, an outer rotor 60, a plurality of vanes 70, and the like.

Here, the inner rotor 50 and the outer rotor 60 form a first pump unit PU1, and the outer rotor 60 and the plurality of vanes 70 form a second pump unit PU2.
Then, as shown in FIG. 3, the compound pump M1 merges 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, the liquid is discharged toward the lubrication area of the application target.

As shown in FIGS. 2 and 5, the base 10 is made of a material such as steel, cast iron, sintered steel, and aluminum alloy, and as shown in FIGS. 2 and 5, a joining surface 10 a that is joined to an object and a joint that is joined to the rotor case 20. It is formed in a flat plate shape that defines the surface 10b.
As shown in FIGS. 2 and 5, the base 10 includes a bearing hole 11, a suction port 12, passages 12 a, 12 b and 12 c communicating with the suction port 12, a discharge port 13, and a passage 13 a communicating with the discharge port 13. The positioning hole 14, four circular holes 15 through which fastening bolts (not shown) for fastening to an object to be applied are provided.

The bearing hole 11 is formed so as to support the drive shaft 40 rotatably around the center line L1.
As shown in FIGS. 2 and 5, the suction port 12 has a substantially crescent-shaped outline indicated by a chain double-dashed 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 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 common suction port so that the oil can be sucked toward.

The passages 12a, 12b, 12c are formed so as to penetrate from the joint surface 10a to the joint surface 10b, similarly to the suction port 12.
As shown in FIG. 5, the passage 12a is formed to guide the oil from the suction port 12 to the supercharging pump chamber C1 of the second pump unit PU2.
As shown in FIG. 5, the passage 12b is formed to guide the oil pressurized in the supercharging pump chamber C1 of the second pump unit PU2 back to the suction port 12 and return it.
As shown in FIG. 5, the passage 12c is formed so as to guide the 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 joint surface of the application object closes the opening on the joint surface 10a side in a state where the composite pump M1 is attached to the application object.
In this way, the passages 12a, 12b, 12c are formed so as to communicate with and penetrate the suction port 12, so that the machining work is facilitated in the case of cutting work, and in the case of molding by a mold. The die cutting becomes easy.
Note that the passages 12a, 12b, 12c may be formed in a groove shape that does not penetrate to the joint surface 10a side, instead of being a through passage as described above.

As shown in FIGS. 2 and 5, the discharge port 13 has a substantially crescent-shaped outline indicated by a chain double-dashed 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 application target, and the oil pressurized by the first pump unit PU1 and the oil pressurized by the second pump unit PU2 and passing through the passage 13a merge and are discharged. Therefore, it is formed as one common discharge port.

The passage 13a is formed so as to penetrate from the joint surface 10a to the joint surface 10b, similarly to the discharge port 13.
As shown in FIG. 5, the passage 13a is formed to guide the oil pressurized in the main pump chamber C2 of the second pump unit PU2 to the discharge port 13.
In the passage 13a, the opening on the joint surface 10a side is closed by the joint surface of the application target in a state where the composite pump M1 is attached to the application target.
Since the passage 13a is formed so as to communicate with and penetrate the discharge port 13 as described above, the machining operation is facilitated in the case of cutting, and the die cutting is performed in the case of molding with a die. It will be easier.
The passage 13a may be formed in a groove shape that does not penetrate to the joint surface 10a side instead of the through passage as described above.

The rotor case 20 is made of a material such as steel, cast iron, and sintered steel, and is joined to the joint surface 20 a and the cover 30 that are joined to the joint surface 10 b of the base 10 as shown in FIGS. 2, 4, and 5. Is formed in a substantially annular shape that defines the joint surface 20b.
As shown in FIG. 2, FIG. 4, and FIG. 5, the rotor case 20 has two inner wall surfaces 21 formed on the inner peripheral surface, two lightening surfaces 22, 23, and a fitting hole into which the positioning pin D is fitted. Further, the screw hole for screwing the screw B is provided with two screw/positioning holes 24 formed coaxially, four circular holes 25 through which fastening bolts are inserted, and the like.

As shown in FIG. 5, the two inner wall surfaces 21 are curved along 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 an arc surface which is the center of the radius and faces each other across the center line L2.
As shown in FIG. 5, the two lightening surfaces 22 and 23 are not in contact with the outer peripheral surface 61 of the outer rotor 60 in a region outside the two inner wall surfaces 21, and cooperate with the outer peripheral surface 61 to substantially eliminate the outer surface 61. It is formed so as to define a space having a crescent shape.

That is, as shown in FIGS. 4 and 5, with the outer rotor 60 incorporated in the rotor case 20, the lightening surface 22 and the outer peripheral surface 61 define the supercharging pump chamber C1 of the second pump unit PU2. It Further, the lightening surface 23 and the outer peripheral surface 61 define the main pump chamber C2 of the second pump unit PU2.

Here, the supercharging pump chamber C1 and the main pump chamber C2 are formed in regions facing each other with the rotation center (center line L2) of the outer rotor 60 interposed therebetween.
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 the regions excluding the regions of the supercharging pump chamber C1 and the main pump chamber C2. In particular, since the outer rotor 60 is supported over a half circumference (180 degrees) or more, the outer rotor 60 can be rotatably and reliably supported.

The cover 30 is made of a material such as steel, cast iron, sintered steel, or aluminum alloy, and is joined to the joining surface 20b of the rotor case 20 to close the opening of the rotor case 20, as shown in FIGS. 1 and 2. It is formed in a flat plate shape that defines the joint surface 30a.
As shown in FIG. 2, the cover 30 has two circular holes 31 through which the screw B is inserted, four circular holes 32 through which fastening bolts are inserted, and the like.

As described above, the housing H is composed of the base 10, the rotor case 20, and the cover 30, and the intake port 12, the discharge port 13, and the passages 12a, 12b, 12c, 13a are provided to the base 10, so that the rotor The case 20 and the cover 30 can have a simple structure.
Further, regarding the relationship with the 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.
Further, by simply changing the base 10, it is possible to easily set not only the increase type composite pump M1 but also the high pressure type composite pump while sharing other parts.

The drive shaft 40 is formed of steel or the like and extends in the direction of the center line L1 as shown in FIGS. 1, 2, and 4.
As shown in FIG. 2, the drive shaft 40 is provided in the connecting portion 41 that transmits the driving force from the application object, the fitting portion 42 that is fitted into the fitting hole 51 of the inner rotor 50, and the fitting portion 42. A through hole 43 or the like is provided in which the detent pin E is fitted.

The inner rotor 50 is made of a material such as steel or sintered steel and slides on the end surface 50a that slides on the joint surface 10b of the base 10 and the joint surface 30a of the cover 30, as shown in FIGS. 2 and 4. It is formed in a substantially star shape that defines the end surface 50b.
As shown in FIGS. 2 and 4, the inner rotor 50 has a tooth profile according to a trochoidal curve, which includes a fitting hole 51, a pin groove 52, four convex portions (peaks) 53 and four concave portions (valleys) 54. It is formed as an external gear.

The fitting hole 51 is formed so that the fitting portion 42 of the drive shaft 40 is fitted therein.
The pin groove 52 is formed so that both sides of the detent pin E inserted into the through hole 43 of the drive shaft 40 are fitted.
Then, the inner rotor 50 rotates counterclockwise in FIG. 4 about the center line L1 as the center of rotation by the drive shaft 40.

The outer rotor 60 is made of a material such as steel or sintered steel, and slides on the end surface 60a that slides on the joint surface 10b of the base 10 and the joint surface 30a of the cover 30, as shown in FIGS. 2 and 4. It is formed in an annular shape that defines the end surface 60b.
As shown in FIGS. 2 and 4, the outer rotor 60 has a circular outer peripheral surface 61 centered on the center line L<b>2, a plurality (here, five) of guide grooves 62 provided on the outer peripheral surface 61, and five guide grooves 62. It is formed as an internal gear having a tooth profile capable of meshing with the inner rotor 50, which is provided with a convex portion 63 and five concave portions 64.

The outer peripheral surface 61 is formed so as to come into contact with the inner wall surface 21 of the rotor case 20 and be rotatably supported.
The five guide grooves 62 are formed at equal intervals (intervals of about 72 degrees) in the circumferential direction. Each guide groove 62 is formed so as to extend outward in the radial direction passing through the center line L2 and open at the outer peripheral surface 61 in a region corresponding to the convex portion 63.
Each of the guide grooves 62 guides the vane 70 so as to be retractable in the radial direction of the outer rotor 60.
In order to make the vane 70 fitted in the guide groove 62 move in and out by the centrifugal force more smoothly, a passage through which oil is passed is partially provided in the side wall of the guide groove 62 so that the vane 70 in the guide groove 62 is located behind the vane 70. May not be 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 in a counterclockwise direction in FIG. 4 with the center line L2 as the center of rotation at a slower speed than the inner rotor 50 while interlocking with the rotation of the inner rotor 50 that rotates about the center line L1. Rotate. Further, the inner rotor 50 and the outer rotor 60 are partially meshed with each other to define a continuously changing pump chamber C therebetween.

The inner rotor 50 and the outer rotor 60 constitute a trochoid pump with four lobes and five nodes as a first pump unit PU1 that sucks oil into the pump chamber C from the suction port 12 and pressurizes it while discharging it to the discharge port 13. ing.

The vane 70 is formed of a material such as steel or sintered steel, and is formed as a cylindrical roller vane as shown in FIGS. 2 and 4.
Then, the vane 70 is fitted in the guide groove 62 of the outer rotor 60 so as to be retractable in the radial direction passing through the center line L2, and a centrifugal force that pops out by the rotation of the outer rotor 60 is generated. The peripheral surfaces (the inner wall surface 21 and the lightening surfaces 22 and 23) move while rolling or sliding.

Thus, by adopting a cylindrical roller vane as the vane 70, the guide groove 62 that guides the vane 70 so that it can be retracted can be set shallower. Therefore, it is possible to prevent the vane 70 from rattling and the like without increasing the outer diameter of the outer rotor 60, that is, without increasing the size, and it is possible to guarantee the desired function.

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, the supercharging pump stroke in which oil is sucked from the suction port 12 through the passage 12a, guided to the supercharging pump chamber C1 and pressurized, and returned to the suction port 12 through the passage 12c is performed. Done. After that, a main pump stroke is performed in which oil is sucked from the suction port 12 through the passage 12c, guided to the main pump chamber C2, pressurized, and discharged to the discharge port 13 through the passage 13a.

The assembling 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 rotation stop pin E are prepared. ..
Subsequently, the rotor case 20 is joined to the base 10 while press-fitting the positioning pin D into (the fitting hole of) the positioning hole 14 and the screw/positioning hole 24.

Then, the inner rotor 50 and the outer rotor 60 are fitted inside the rotor case 20, and the five vanes 70 are fitted in the guide grooves 62 of the outer rotor 60.
Subsequently, the rotation stop pin E is inserted into the through hole 43 of the drive shaft 40, the drive shaft 40 is passed through the fitting hole 51 and the bearing hole 11, and the fitting portion 42 is fitted into the fitting hole 51 and is rotated. The stop pin E is fitted into the pin groove 52.
As a result, the drive shaft 40 and the inner rotor 50 rotate together.
When the connecting portion 41 of the drive shaft 40 is larger than the shaft diameter, the drive shaft 40 may be inserted from the joint surface 10a side of the base 10 and then the rotation stop pin E may be inserted.

Finally, the cover 30 is joined to the joining surface 20b of the rotor case 20, and the two screws B are screwed into (the screw holes of) the screw/positioning hole 24.
As described above, the assembly of the composite pump is completed.
In this way, the housing H is composed of the base 10, the rotor case 20, and the cover 30, so that the assembly work when handling the composite pump M1 as a product can be easily performed.
When the composite pump M1 is attached to the application object, the joint surface 41 of the base 10 contacts the joint surface of the application object while connecting the connecting portion 41 of the drive shaft 40 to the connection portion of the application object. Let Thereafter, the fastening bolt is passed through the circular holes 32, 25, 15 and is screwed into the threaded hole of the application target, whereby the mounting work is completed.

Next, the operation of the composite pump M1 will be described with reference to FIGS. 6(a) and (b) to FIGS. 9(a) and 9(b). 6(a), 6(b) to 9(a), 9(b) show the operating state 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 focusing on the front side and the rear side in the rotation direction of one vane 70 (marked with a black circle).
At the position shown in FIG. 6( a ), on the rear side of the vane 70, oil begins to be sucked into the supercharging pump chamber C 1 from the suction port 12 through the passage 12 a, and on the front side of the vane 70, the supercharging pump chamber is preceded by oil. The oil sucked into C1 begins to return toward the suction port 12 through the passage 12b while being pressurized.
Subsequently, when the drive shaft 40 rotates a predetermined angle after passing through the intermediate state shown in FIG. 6B, at the position shown in FIG. The oil suction operation ends, and the return operation from the supercharging pump chamber C1 to the suction port 12 ends on the front side of the vane 70 (supercharging pump stroke).

Subsequently, when the drive shaft 40 rotates a predetermined angle after the inactive state (no pump operation) shown in FIG. 7B, the suction is performed at the rear side of the vane 70 at the position shown in FIG. 8A. Oil starts to be sucked into the main pump chamber C2 from the mouth 12 through the passage 12c, and in front of the vane 70, the oil previously sucked into the main pump chamber C2 is pressurized and is discharged to the discharge port 13 through the passage 13a. Aiming to be discharged.
Subsequently, when the drive shaft 40 rotates a predetermined angle after passing through the intermediate state shown in FIG. 8B, the suction into the main pump chamber C2 at the rear side of the vane 70 at the position shown in FIG. 9A. The operation ends, and the discharge operation from the main pump chamber C2 to the discharge port 13 ends on the front side of the vane 70 (main pump stroke).

Subsequently, when the drive shaft 40 rotates a predetermined angle after the inactive 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 given focusing on one vane 70, but in reality, the five vanes 70 respectively perform similar operations (supercharging pump stroke and main pump stroke).
Therefore, in 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 focusing on the front side and the rear side in the rotation direction of one convex portion 53 (marked with a black circle).
When the drive shaft 40 rotates a predetermined angle after the inactive state (no pump operation) shown in FIG. 6A, the suction port 12 is provided at the position shown in FIG. Is in a state immediately before starting to suck oil, and on the front side of the convex portion 53, oil is being sucked into the pump chamber C from the suction port 12.

Subsequently, when the drive shaft 40 rotates a predetermined angle after passing through the intermediate state shown in FIG. 7A, at the position shown in FIG. 7B, on the rear side of the convex portion 53, from the suction port 12 to the pump chamber C. The oil is in the middle of being sucked into the inside of the convex portion 53, and 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 the oil is discharged toward the discharge port 13.

Subsequently, when the drive shaft 40 rotates a predetermined angle after passing through the intermediate state shown in FIG. 8A, at the position shown in FIG. 8B, in front of the convex portion 53, the pump chamber is directed toward the discharge port 13. The oil is in the middle of being discharged from the inside of C, and on the rear side of the convex portion 53, the state is just before the oil suction from the suction port 12 ends and immediately before the discharge toward the discharge port 13.

Subsequently, when the drive shaft 40 rotates a predetermined angle after passing through the intermediate state shown in FIG. 9A, at the position shown in FIG. 9B, from the pump chamber C to the discharge port 13 on the front side of the convex portion 53. The discharging operation of is finished.
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 given by focusing on one convex portion 53, but in reality, the four convex portions 53 respectively perform the same operation (pump stroke).
Therefore, the first pump unit PU1 performs the discharge operation four times 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, the discharge timing of the first pump unit PU1 and the discharge timing of the second pump unit PU2 are as shown in FIG. The other is set to a different phase, which is shifted by 90 degrees.
According to this, since the second pump unit PU2 is set to discharge in the region where the first pump unit PU1 does not discharge or the region where the discharge amount decreases, the discharge pulsation can be reduced, and the smoothed and stable discharge can be achieved. You can get the quantity.

Further, in the process of the operation shown in FIGS. 6A to 7A, the second pump unit PU2 performs the supercharging pump stroke.
Therefore, in 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. Further, in the first pump unit PU1, the oil pressure is increased by the amount of supercharging at the time of suction, and it is possible to prevent the occurrence of cavitation and the like.

As described above, according to the composite pump M1 according to the above-described embodiment, cavitation or the like occurs while achieving simplification of structure, miniaturization, cost reduction, reduction of driving load by reduction of sliding area, and the like. And a desired pump performance can be secured, and an increase type composite pump capable of increasing the discharge amount can be obtained.

Next, the composite pump M2 according to the second embodiment will be described with reference to FIGS. The composite pump M2 is a high-pressure pump that multi-stages and supplies oil as a fluid in a lubrication system of an application object such as an engine and a transmission.
The same components as those of the composite pump M1 according to the above-described embodiment are designated by the same reference numerals and description thereof will be omitted.

As shown in FIGS. 11 to 14, the compound pump M2 includes a housing H′ including a base 10′, a rotor case 20′, and a cover 30′, a drive shaft 40, an inner rotor 50, an outer rotor 60, and a plurality of vanes. 70 and so on.

The base 10 ′ is substantially the same as the base 10 except that it has a different shape, and as shown in FIGS. 12 to 14, the bearing hole 11, the suction port 12, the passages 12 a and 12 b communicating with the suction port 12, and the discharge port 12. An outlet 13', two positioning holes 14, four circular holes 15, a substantially L-shaped passage 16', etc. are provided.

As shown in FIGS. 12, 13, and 14(b), the discharge port 13' has a long contour 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 for discharging the oil multi-stage pressurized by the first pump unit PU1 and the second pump unit PU2 through the passage 26'. Has been formed.

As shown in FIGS. 13 and 14(a), the passage 16′ has a substantially L-shaped groove shape in which the joint surface 10b side of the base 10′ is thinned to a predetermined depth, and the passage 16′ of the first pump unit PU1. The oil pressurized in the pump chamber C is formed so as to be guided to the main pump chamber C2 of the second pump unit PU2.

The rotor case 20 ′ is substantially the same as the rotor case 20 except that the shape thereof is different. As shown in FIGS. 12 to 14, two inner wall surfaces 21 and two lightening surfaces 22, 23 and two screws are used. The positioning hole 24, the four circular holes 25, and the passage 26' are provided.
The passage 26' is formed by partially thinning the oil so as to guide the oil pressurized in the main pump chamber C2 of the second pump unit PU2 to the discharge port 13'.

The cover 30 ′ is substantially the same as the cover 30 except that the shape is different, and includes two circular holes 31, four circular holes 32 and the like.

Then, as shown in FIG. 11, the compound pump M2 guides the oil pressurized by the first pump unit PU1 to the second pump unit PU2 via the oil pan OP and the passage of the object to be applied, and the second pump unit PU2. The oil further pressurized in (1) is discharged toward the lubrication area of the application target.

Next, the operation of the composite pump M2 will be described with reference to FIGS. 15(a), (b) to 18(a), (b). 15(a), 15(b) to 18(a), 18(b) show the operating state for each time series when the drive shaft 40 rotates counterclockwise.
Here, 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, one vane 70 (marked with a black circle) in the second pump unit PU2 and one convex portion 53 (marked with a black circle) in the first pump unit PU1 are disposed on the front side and the rear side in the rotation direction. The explanation will be focused on.

At the position shown in FIG. 15( a ), on the rear side of the vane 70, there is a state immediately before the oil starts to be sucked into the supercharging pump chamber C 1 from the suction port 12 through the passage 12 a, and on the front side of the vane 70, It is in a state immediately before the oil sucked into the supercharging pump chamber C1 is pressurized and begins to be returned toward the suction port 12 via the passage 12b.
Further, the convex portion 53 is in a non-actuated state (no pump operation) at the position shown in FIG.

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

Then, when the drive shaft 40 rotates by a predetermined angle, at the position shown in FIG. 16( a ), the operation of sucking oil into the supercharging pump chamber C<b>1 ends on the rear side of the vane 70 and the front side of the vane 70. The returning operation from the supercharging pump chamber C1 to the suction port 12 is completed (supercharging pump stroke).
Further, on the rear side and the front side of the convex portion 53, the oil is being 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 the inoperative state at the position shown in FIG. 16(b). Further, on the rear side of the convex portion 53, oil is being sucked into the pump chamber C from the suction port 12, and on the front side of the convex portion 53, at the same time when the oil suction operation into the pump chamber C is completed. The state is just before the oil is discharged toward the passage 16'.

Then, when the drive shaft 40 rotates by a predetermined angle, the vane 70 is in the inoperative state at the position shown in FIG. On the rear side of the convex portion 53, oil is being sucked into the pump chamber C from the suction port 12, and on the front side of the convex portion 53, the oil in the pump chamber C is discharged toward the passage 16'. It is in the process of being processed.

Then, when the drive shaft 40 rotates by a predetermined angle, the vane 70 is in the inoperative state at the position shown in FIG. 17(b). On the rear side of the convex portion 53, the state immediately before the oil is discharged toward the passage 16 ′ is reached at the same time when the operation of sucking the oil from the suction port 12 into the pump chamber C is completed. Then, the oil in the pump chamber C is in the process of being guided into the main pump chamber C2 through the passage 16'.

Then, when the drive shaft 40 rotates by a predetermined angle, oil starts to be sucked into the main pump chamber C2 through the passage 16′ at the rear side of the vane 70 at the position shown in FIG. Then, the oil previously sucked into the main pump chamber C2 starts to be discharged to the discharge port 13' through the passage 26' while being further pressurized (main pump stroke).

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

Although one vane 70 and one convex portion 53 have been described here, the five vanes 70 actually perform the same operation (supercharging pump stroke, main pump stroke) and four vanes. The convex portions 53 perform 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 process of the operation shown in FIGS. 15A to 16A, the second pump unit PU2 performs the supercharging pump stroke.
Therefore, in 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. Further, in the first pump unit PU1, the oil pressure is increased by the amount of supercharging at the time of suction, and it is possible to prevent the occurrence of cavitation and the like.

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 structure, downsizing, cost reduction, reduction of driving load by reduction of sliding area, and the like. It is possible to obtain a high-pressure type composite pump that can prevent the occurrence of the above-mentioned problem and can secure desired pump performance and can increase the discharge pressure.

In the above embodiment, the case where the second pump unit PU2 includes the supercharging pump stroke has been described. However, the present invention is not limited to this, and the supercharging pump stroke (passages 12a, 12b) is abolished when the initial suction performance of the vane pump or the like is secured and cavitation or the like of the trochoid pump is resolved. The second pump unit PU2' can also be adopted.
And as shown in FIG. 19, you may employ|adopt the increase type compound pump M1' which employ|adopted the 2nd pump unit PU2'.
Further, as shown in FIG. 20, a high-pressure type 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 trochoidal pump having the trochoidal tooth shape 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 shape, or an inner rotor and an outer rotor having other tooth shapes.

In the above embodiment, the inner rotor 50 and the outer rotor 60 are composed of trochoidal four-lobed five-nodes, and the plurality of vanes 70 are composed of five vanes. However, the present invention is not limited to this. A configuration including the number of

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' is shown, but the present invention is not limited to this. Instead, the base and the rotor case may be integrated.

In the above embodiment, the composite pumps M1 and M2 each include the drive shaft 40, but the configuration is not limited to this. For example, if the drive shaft can be assembled after the housing is assembled, the composite pump may be constructed without the drive shaft.

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

M1, M1', M2, M2' Composite pump PU1 1st pump unit PU2, PU2' 2nd pump unit H Housing 10, 10' Base (housing)
10a, 10b Joint surface 11 Bearing hole 12 Suction port 12a, 12b, 12c Passage 13, 13' Discharge port 13a Passage 14 Positioning hole 15 Circular hole 16' Passage 20, 20' Rotor case (housing)
20a, 20b Joining surface 21 Inner wall surface 22, 23 Lightening surface 24 Screw/positioning hole 25 Circular hole 26' Passage 30, 30' Cover (housing)
30a Bonding surface 31 Circular hole 32 Circular hole 40 Drive shaft L1 Center line (center of rotation)
41 connecting part 42 fitting part 43 through hole 50 inner rotor (first pump unit)
50a, 50b End surface 51 Fitting hole 52 Pin groove 53 Convex portion 54 Recessed portion 60 Outer rotor (first pump unit, second pump unit)
L2 center line (rotation center)
60a, 60b End surface 61 Outer peripheral surface 62 Guide groove 63 Convex portion 64 Recessed portion 70 Vane (roller vane, second pump unit)
B Screw D Positioning pin E Non-rotating pin

Claims (10)

Housing,
A first pump unit that is disposed in the housing and includes an inner rotor and an outer rotor that mesh with each other;
A second pump unit that is disposed in the housing and that includes a plurality of vanes that can be projected and retracted in the radial direction on the 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 discharge port through which fluid pressurized by the first pump unit and the second pump unit is discharged. have a discharge port,
The operation of the second pump unit includes a supercharging pump stroke for returning the fluid pressurized and sucked from the suction port to the suction port side, and the fluid sucked and pressurized from the suction port to the discharge port. Including the main pump stroke to discharge
The housing includes a supercharging pump chamber corresponding to the supercharging pump stroke, and a main pump chamber corresponding to the main pump stroke,
A composite pump characterized in that The vane is a roller vane formed in a cylindrical shape,
The composite pump according to claim 1, wherein: The supercharging pump chamber and the main pump chamber are formed in regions facing each other with the center of rotation of the outer rotor interposed therebetween.
The composite pump according to claim 1 or 2 , characterized in that. The housing has a passage for merging the fluid pressurized by the first pump unit with the fluid pressurized by the second pump unit and guiding the fluid to the discharge port.
The composite pump according to any one of claims 1 to 3, 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 4 , wherein: 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 3, wherein: The housing includes a base that defines the suction port, the discharge port, and the passage, a rotor case that rotatably supports the outer circumference of the outer rotor, and a cover that closes an opening of the rotor case. ,
The composite pump according to claim 4 , wherein: The housing includes a base that defines the suction port, the discharge port, and the two passages, a rotor case that rotatably supports the outer circumference of the outer rotor, and a cover that closes an opening of the rotor case. including,
The composite pump according to claim 6 , wherein: A drive shaft rotatably supported by the housing and connected to the inner rotor;
The composite pump according to any one of claims 1 to 8, which is characterized in that. The inner rotor and the outer rotor of the first pump unit are composed of trochoidal 4-lobed 5-node,
The plurality of vanes of the second pump unit are composed of five vanes arranged at equal intervals on the outer circumference of the outer rotor,
The composite pump according to any one of claims 1 to 9 , characterized in that.

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