WO2023037875A1

WO2023037875A1 - Variable capacity-type oil pump

Info

Publication number: WO2023037875A1
Application number: PCT/JP2022/031801
Authority: WO
Inventors: 暢昭寒川; 浩二佐賀
Original assignee: 日立Astemo株式会社
Priority date: 2021-09-10
Filing date: 2022-08-24
Publication date: 2023-03-16
Also published as: CN117940669A; JPWO2023037875A1

Abstract

This variable capacity-type oil pump comprises: a connection path (31) linearly formed at a position adjacent to a first chamber (26) and a second chamber (27) when viewed in a direction along the rotation axis (O1) of a pump structure; a first chamber oil path (32) which branches from the connection path (31) and is connected to the first chamber (26); and a second chamber oil path (34) which branches from the connection path (31) and is connected to the second chamber (27). In addition, a valve section (28) of a solenoid valve (13) is inserted into a control valve accommodation section (30) provided in a block section (1k), the valve section including a part of the connection path (31).

Description

Variable displacement oil pump

The present invention relates to a variable displacement oil pump.

As a variable displacement oil pump, for example, a variable displacement oil pump described in Patent Document 1 below is known.

The variable displacement oil pump described in Patent Document 1 has a discharge section that discharges oil to a main gallery, and when the oil from the main gallery is introduced and the adjustment member moves in the direction in which the oil from the discharge section decreases, A first chamber whose volume increases, and a second chamber whose volume increases when oil from the main gallery is introduced through the control valve and the adjustment member moves in the direction in which the pressure of the oil discharged from the discharge port increases. room and,

WO2020/071061

In the variable displacement oil pump described in Patent Document 1, oil passages for guiding oil from the main gallery to the first and second chambers are formed intricately inside the housing.

SUMMARY OF THE INVENTION The present invention has been devised in view of the conventional circumstances, and provides a variable displacement oil pump capable of easily forming an oil passage for guiding oil from a main gallery to a first chamber or a second chamber. It is intended to

In the present invention, the variable displacement oil pump includes a connecting passage formed linearly at a position adjacent to the first chamber and the second chamber when viewed from the direction along the rotation axis of the pump structure, and the connecting passage. A first chamber oil passage branched in a direction intersecting the longitudinal direction of the passage and connected to the first chamber, and a second chamber oil passage branched in a direction intersecting the longitudinal direction of the connection passage from the control valve accommodating portion and connected to the second chamber. and a two-chamber oil passage, and a control valve is inserted into the control valve housing.

According to the present invention, it is possible to easily form oil passages for guiding oil from the main gallery to the first and second chambers.

1 is an exploded perspective view of a variable displacement oil pump according to a first embodiment; FIG. 1 is a front view of a variable displacement oil pump according to a first embodiment; FIG. FIG. 3 is a perspective view of a housing main body in which a cam ring, an electromagnetic valve, etc. are accommodated; (a) is a cross-sectional view of an electromagnetic valve housed in a control valve housing, and (b) is a cross-sectional view of a valve body cut along line AA in (a). It is a cross-sectional view of the variable displacement oil pump showing the first state of the solenoid valve. FIG. 4 is a cross-sectional view of the variable displacement oil pump showing a second state of the solenoid valve; FIG. 4 is a characteristic diagram showing the correlation between the engine speed and the main gallery pressure of the variable displacement oil pump of the first embodiment; It is a sectional view of the solenoid valve of a 2nd embodiment. FIG. 11 is a front view of the variable displacement oil pump of the third embodiment showing the non-operating state of the solenoid valve; FIG. 11 is a front view of the variable displacement oil pump of the third embodiment, showing the operating state of the solenoid valve; FIG. 11 is a front view of the variable displacement oil pump of the fourth embodiment showing the non-operating state of the solenoid valve; FIG. 11 is a front view of a variable displacement oil pump according to a fourth embodiment, showing operating states of solenoid valves;

An embodiment of the variable displacement oil pump of the present invention will be described below with reference to the drawings.

[First embodiment]
(Configuration of variable displacement oil pump)
FIG. 1 is an exploded perspective view of a variable displacement oil pump according to a first embodiment provided in a cylinder block or the like of an internal combustion engine (not shown). FIG. 2 is a front view of the variable displacement oil pump of the first embodiment with the front cover removed. FIG. 3 is a perspective view of the housing body 1 in which the cam ring 6, the solenoid valve 13 and the like are accommodated. In FIG. 3, the components inside the cam ring 6 are omitted to clarify the flow paths such as the connection path 31, and the housing body 1 is shown by schematic phantom lines.

The variable displacement oil pump includes a housing consisting of a housing body 1 and a cover member 2, a drive shaft 3, a rotor 4, a plurality of (seven in this embodiment) vanes 5, and a cam ring 6 as an adjusting member. , a first coil spring 7, a pair of ring members 8, first to third sealing means 9 to 11, and five fixing means such as a screw member 12, an electromagnetic valve 13, and a relief valve 14. ing.

The housing body 1 is integrally formed of a metal material, such as an aluminum alloy material, and is formed into a cylindrical shape with a bottom so that one end side is open and a pump accommodating chamber 1a recessed in a substantially cylindrical shape is provided therein. there is As shown in FIG. 1, the housing body 1 has a first bearing hole 1c that rotatably supports one end of the drive shaft 3 at the center of the bottom surface 1b of the pump housing chamber 1a. The housing body 1 is formed with an annularly continuous flat mounting surface 1d on the outer peripheral side of the opening of the pump accommodating chamber 1a. The mounting surface 1d of the housing body 1 is formed with five screw holes 1e into which the respective screw members 12 are screwed.

Like the housing body 1, the cover member 2 is made of a metal material, such as an aluminum alloy material, and is used to close the opening of the housing body 1. The cover member 2 has a flat plate shape and has an outer shape corresponding to the outer shape of the housing body 1 . A second bearing hole 2 a is formed in the cover member 2 at a position corresponding to the first bearing hole 1 c of the housing body 1 to rotatably support the other end of the drive shaft 3 . Further, on the outer peripheral portion of the cover member 2, at positions corresponding to the five screw holes 1e of the housing body 1, five fixing means through-holes 2b (four fixing means in FIG. through holes 2b) are formed respectively.

The housing main body 1 and the cover member 2 constitute a housing that partitions the pump accommodating chamber 1a.

The drive shaft 3 passes through the center of the pump housing chamber 1a and is rotatably supported by the housing, and is rotationally driven by a crankshaft (not shown). The drive shaft 3 rotates the rotor 4 counterclockwise in FIG. 2 by a rotational force transmitted from the crankshaft.

The rotor 4 has a cylindrical shape and is rotatably accommodated in the pump accommodation chamber 1a. A central portion of the rotor 4 is coupled to the drive shaft 3 . As shown in FIGS. 1 and 2, the rotor 4 is formed with seven slits 4a radially extending from the inner center side of the rotor 4 to the outside in the radial direction. As shown in FIGS. 1 and 2, back pressure chambers 4b each having a circular cross section are formed at the inner base ends of the respective slits 4a to introduce the discharge oil discharged to the discharge ports 24, which will be described later. . As shown in FIG. 2 , the back pressure chamber 4 b opens into circular recesses 4 c formed on both side surfaces of the rotor 4 . Oil from a second chamber 27, which will be described later, flows into the back pressure chamber 4b via the discharge port 24, an oil introduction groove (not shown) formed in the bottom surface 1b of the pump housing chamber 1a, and the circular recess 4c. As a result, the vanes 5 retractably accommodated in the slits 4a of the rotor 4 are pushed outward by the centrifugal force accompanying the rotation of the rotor 4 and the hydraulic pressure in the back pressure chamber 4b.

The vanes 5 are made of metal in the form of thin plates, and are accommodated in the slits 4a of the rotor 4 so as to be retractable. A small gap is formed between the vane 5 and the slit 4a when the vane 5 is accommodated in the slit 4a. When the rotor 4 rotates, the vanes 5 slidably contact the inner peripheral surface of the cam ring 6 at the tip end surfaces and slidably contact the outer peripheral surface of the ring member 8 at the inner end surfaces of the base ends. As a result, even when the engine speed is low and the centrifugal force and the hydraulic pressure in the back pressure chamber 4b are small, the vanes 5 slidably come into contact with the inner peripheral surface of the cam ring 6, and each pump chamber 15 is liquid-tightly defined. It is designed to be

The drive shaft 3, rotor 4, and vanes 5 constitute a pump structure. A cam ring 6 surrounding this pump structure is integrally formed in a cylindrical shape from sintered metal. A first coil spring 7 positioned on the outer periphery of the cam ring 6 is housed in the housing body 1 and always biases the cam ring 6 in a direction to increase the eccentricity of the cam ring 6 with respect to the rotation center of the rotor 4 . A ring member 8 is slidably arranged in a circular concave portion 4c provided in the rotor 4. As shown in FIG.

The first to third seal means 9 to 11 are mounted on the cam ring 6 so as to be slidable on the first to third

seal contact surfaces

1g, 1h and 1i, and partition the cam ring 6 and the housing body 1. As a result, first and

second chambers

26 and 27, which are control hydraulic chambers and will be described later, are fluid-tightly defined between the outer peripheral surface of the cam ring 6 and the inner peripheral surface of the housing body 1 . The first sealing means 9 includes a first sealing member 16 and a first elastic member 17 that biases the first sealing member 16 toward the inner peripheral surface of the housing body 1 . The second seal means 10 also includes a second seal member 18 and a second elastic member 19 that biases the second seal member 18 toward the inner peripheral surface of the housing body 1 . Also, the third sealing means 11 includes a third sealing member 20 and a third elastic member 21 that biases the third sealing member 20 toward the inner peripheral surface of the housing body 1 .

As shown in FIG. 1, a circular support hole 1f for rockably supporting the cam ring 6 via a cylindrical pivot pin 22 is formed at a predetermined position on the inner peripheral wall of the pump housing chamber 1a. Here, for the convenience of the following explanation, in FIG. cam ring reference line M”.

As shown in FIG. 2, the inner peripheral wall of the pump accommodating chamber 1a is formed with a first seal contact surface 1g in a region on one side (right side in FIG. 2) of the cam ring reference line M. A first seal member 16 provided on the outer periphery of the cam ring 6 is slidably brought into contact with the first seal contact surface 1g. As shown in FIG. 2, the first seal contact surface 1g is an arcuate surface having a predetermined radius R1 from the center O2 of the pivot pin 22. As shown in FIG. The radius R1 is set to a circumferential length that allows the first seal member 16 to always slidably contact within the eccentric swing range of the cam ring 6 .

Similarly, as shown in FIG. 2, a second seal contact surface 1h is formed on the inner peripheral wall of the pump housing chamber 1a in a region on the other side (left side in FIG. 2) of the cam ring reference line M. A second seal member 18 provided on the outer periphery of the cam ring 6 is slidably brought into contact with the second seal contact surface 1h. As shown in FIG. 2, the second seal contact surface 1h is an arcuate surface formed from the center O2 of the pivot pin 22 with a predetermined radius R2 smaller than the radius R1. The radius R2 is set to a circumferential length that allows the second seal member 18 to always slidably contact within the eccentric swing range of the cam ring 6 .

Further, as shown in FIG. 2, a third seal contact surface is formed on the inner peripheral wall of the pump housing chamber 1a at a position farther from the pivot pin 22 than the second seal contact surface 1h in the region on the left side of the cam ring reference line M. 1i is formed. A third seal member 20 provided on the outer periphery of the cam ring 6 is slidably brought into contact with the third seal contact surface 1i. As shown in FIG. 2, the third seal contact surface 1i is an arcuate surface extending from the center O2 of the pivot pin 22 with a predetermined radius R3 larger than the radius R1. The radius R3 is set to a circumferential length that allows the third seal member 20 to always slidably contact within the eccentric swing range of the cam ring 6 .

As shown in FIG. 2, on the bottom surface 1b of the pump housing chamber 1a, a suction port 23, which is an arc-shaped concave suction portion, and a discharge port 24, which is also an arc-shaped concave discharge portion, are provided on the outer peripheral region of the drive shaft 3. are cut so as to face each other with the drive shaft 3 interposed therebetween. The suction port 23 is located on the opposite side of the pivot pin 22 on the bottom surface 1b, and opens to a region (suction region) where the internal volume of the pump chamber 15 (to be described later) increases due to the pumping action of the pump structure. ing.

A suction groove (not shown) having the same shape as the suction port 23 is formed on the inner surface of the cover member 2 at a position corresponding to the suction port 23 . It communicates with the suction hole 2c (see FIG. 1) provided in the . As a result, the oil stored in the oil pan of the internal combustion engine (not shown) flows into the suction region through the suction hole 2c and the suction groove of the cover member 2 based on the negative pressure generated by the pump action of the pump assembly. is sucked into each pump chamber 15.

On the other hand, the discharge port 24 is located on the pivot pin 22 side and opens in a region (discharge region) where the internal volume of the pump chamber 15 decreases due to the pump action of the pump structure. In the vicinity of the starting end of the discharge port 24, as shown in FIG. 1, a discharge hole 1j having a circular cross section is provided which penetrates the side wall of the housing body 1 and opens to the outside. As a result, the oil pressurized by the pumping action and discharged to the discharge port 24 flows from the discharge hole 1j through the discharge passage (not shown) and the main gallery (not shown) to each slide of the internal combustion engine (not shown). parts, valve timing devices, etc. A discharge groove (not shown) having the same shape as the discharge port 24 is formed on the inner surface of the cover member 2 at a position corresponding to the discharge port 24 .

Further, in the housing body 1 , a spring housing the first coil spring 7 is located between the second seal member 18 and the third seal member 20 at a position facing the flat portion 6 a provided on the outer periphery of the cam ring 6 . A storage chamber 25 is provided. In the spring accommodating chamber 25, the first coil spring 7 compressed by a predetermined set load W1 is elastically in contact with one end wall of the spring accommodating chamber 25 and the flat portion 6a. In this manner, the first coil spring 7 constantly moves the cam ring 6 through the flat portion 6a in the direction in which the eccentricity increases (counterclockwise direction in FIG. 2) with the elastic force based on the set load W1. energize.

Further, as shown in FIG. 2, the outer peripheral portion of the cam ring 6 has first to third seal surfaces at positions facing the first to third seal contact surfaces 1g to 1i. Portions 6b to 6d protrude respectively. Here, the first to third seal surfaces have predetermined radii slightly smaller than the radii R1, R2, R3 forming the corresponding

seal contact surfaces

1g, 1h, 1i from the center O2 of the pivot pin 22. It is composed by A small clearance is formed between each seal surface and each

seal contact surface

1g, 1h, 1i. First and second

seal holding grooves

6e, 6f, and 6g each having a U-shaped cross section are formed along the axial direction of the cam ring 6 on the seal surfaces of the

seal holding portions

6b, 6c, and 6d, respectively. . In the first to third seal holding grooves 6e to 6g, first to

third seal members

16, 18, 20 contact the first to third

seal contact surfaces

1g, 1h, 1i when the cam ring 6 eccentrically swings. retained respectively.

Further, in the outer peripheral area of the cam ring 6, a first chamber 26 is defined by the outer peripheral portion of the substantially circular support wall portion 6j of the cam ring 6 surrounding the pivot pin 22 and the first seal member 16. A second chamber 27 is defined by the seal member 18 and the third seal member 20 . Pump discharge pressure is introduced into the first chamber 26 via a first chamber oil passage 32, which will be described later. A pump discharge pressure is supplied via an oil passage 34 . The volume of the first chamber 26 increases when the oil discharged from the discharge port 24 is guided and the cam ring 6 moves in the direction in which the flow rate of the oil discharged from the discharge port 24 decreases. there is The second chamber 27 is a space that includes the spring housing chamber 25, and is configured so that its volume increases when the cam ring 6 moves in the direction in which the flow rate of the oil discharged from the discharge port 24 increases. ing.

Of the outer peripheral surface of the cam ring 6, the surface adjacent to the first chamber 26 serves as a first pressure receiving surface 6h that receives the pump discharge pressure introduced into the first chamber 26. A surface of the outer peripheral surface of the cam ring 6 adjacent to the second chamber 27 serves as a second pressure receiving surface 6i (including the flat portion 6a) that receives the pump discharge pressure introduced into the second chamber 27. As shown in FIG.

When each pump discharge pressure acts on the corresponding first and second

pressure receiving surfaces

6h, 6i of the cam ring 6, the urging force based on the hydraulic pressure acting on the first and second

pressure receiving surfaces

6h, 6i and the first The amount of eccentricity of the cam ring 6 is controlled by the balance with the biasing force of the coil spring 7 . Here, the pressure receiving area of the first pressure receiving surface 6h is set larger than the pressure receiving area of the second pressure receiving surface 6i, and when hydraulic pressure acts on both

pressure receiving surfaces

6h and 6i, the eccentricity as a whole decreases. The cam ring 6 is urged in the direction.

The solenoid valve 13 corresponds to the control valve of the present invention, and controls the axial position of the spool 40 by supplying and discharging oil according to the axial position of the spool 40 in the moving direction, which will be described later. A solenoid portion 29 is provided. The solenoid valve 13 is provided on a regular hexahedral block portion 1k integrally formed on the rear surface of the housing body 1 as shown in FIG. More specifically, the valve portion 28 located on the tip side of the solenoid valve 13 is housed in a control valve housing portion 30 recessed with respect to one surface 1m of the block portion 1k as shown in FIG. A solenoid portion 29 located on the rear end side of 13 protrudes outward from the surface 1m of the block portion 1k. When the valve portion 28 is housed in the control valve housing portion 30, as shown in FIG. The area of the cam ring 6 between the chamber 26 and the second chamber 27 overlaps, and the solenoid portion 29 is positioned outside the second chamber 27 . In other words, when viewed along the rotation axis O1 of the pump assembly as shown in FIG. , and the solenoid portion 29 is provided so as not to face the second chamber 27 . The various components and functions of solenoid valve 13 will be described in detail later.

As shown in FIG. 2, the housing main body 1 is located on the center axis Z of the solenoid valve 13 when viewed from the direction along the rotation axis O1 of the pump structure, and oil from the main gallery is supplied to the main gallery. A linear connecting passage (straight oil passage portion) 31 (indicated by a phantom line) guided through the introduction port 33 and the first chamber oil passage 32 is formed. As shown in FIG. 2, the connection path 31 is provided at a position adjacent to the pivot pin 22 in the region between the pivot pin 22, which is the swing fulcrum of the cam ring 6, and the drive shaft 3 of the pump assembly. In other words, the connection path 31 extends along the central axis Z between a portion P1 of the first chamber 26 located on the pivot pin 22 side and a portion P2 of the second chamber 27 located on the pivot pin 22 side in the radial direction with respect to the rotation axis O1. It is provided to be connected at the shortest distance along the The outer diameter of the connection path 31 is set smaller than the inner diameter of the control valve accommodating portion 30 .

Also, as shown in FIG. 3, one end of the connection path 31 is connected to the first chamber 26 via a first chamber oil path 32 branched in a direction crossing the longitudinal direction of the connection path 31 . More specifically, one end of the connection path 31 is connected to the first chamber 26 via a first chamber oil path 32 branched perpendicular to the longitudinal direction of the connection path 31 . The first chamber oil passage 32 opens toward the first chamber 26 at a point P1 above the first chamber 26 when viewed from the direction along the rotation axis O1 as shown in FIG. Further, as shown in FIG. 3, the outer peripheral portion of the first chamber oil passage 32 is located near the connection passage 31 between the first chamber 26 and the connection passage 31, and an introduction port 33 through which oil from the main gallery is introduced. It is connected to the. As shown in FIG. 3, the introduction port 33 extends to the outer peripheral portion of the first chamber oil passage 32 so as to be perpendicular to the surface 1n of the housing body 1 on which the discharge holes 1j are provided. Oil from the main gallery is introduced into the first chamber 26 via an inlet 33 and a first chamber oil passage 32 .

As shown in FIG. 3, the other end (not shown) of the connecting passage 31 passing through the solenoid valve 13 is connected to a second chamber oil passage 34 branched in a direction intersecting the longitudinal direction of the connecting passage 31. It is connected to 2 rooms 27. More specifically, the other end of the connection path 31 is connected to the second chamber 27 via a second chamber oil path 34 branched in a direction orthogonal to the longitudinal direction of the connection path 31 . As shown in FIG. 3 , the second chamber oil passage 34 extends parallel to the first chamber oil passage 32 . The second chamber oil passage 34 opens toward the second chamber 27 at a point P2 above the second chamber 27 when viewed from the direction along the rotation axis O1 as shown in FIG. Oil from the main gallery is introduced into the second chamber 27 via the introduction port 33 , the first chamber oil passage 32 , the connection passage 31 and the second chamber oil passage 34 .

The relief valve 14 is housed in a valve housing hole 35 (indicated by phantom lines in FIG. 2) formed in the vicinity of the discharge port 24, as shown in FIG. It functions to release the discharge pressure to the outside by opening the valve when the pressure is high. The relief valve 14 includes a lid 36 closing the valve housing hole 35 , a spring 37 having one end in contact with the lid 36 , and a ball 38 having the other end in contact with the spring 37 . When the discharge pressure of the variable displacement oil pump is higher than a predetermined discharge pressure, the discharge pressure acts on the ball 38, and when the ball 38 contracts the spring 37 against the lid 36, the back side of the ball 38 The discharge pressure is released to the outside through a relief hole (not shown) provided.
(Configuration of solenoid valve)
4(a) is a sectional view of the solenoid valve 13 housed in the control valve housing portion 30, and FIG. 4(b) is a valve body 39 cut along the line AA in FIG. 4(a). is a cross-sectional view of.

As shown in FIG. 4( a ), the control valve housing portion 30 has a bottom portion 30 a with an open connection path 31 and a conical bottom portion 30 a that expands in diameter toward the solenoid portion 29 , and the bottom portion 30 a is axially opposed to the bottom portion 30 a. and a control valve receiving port 30b formed at a position. The valve portion 28 of the solenoid valve 13 is inserted into the control valve housing portion 30 from the control valve housing port 30b toward the bottom portion 30a.

Here, the connection path 31 actually includes a tip side passage 31b, an axial passage 31c, a first valve opening 31d, an introduction passage 31e, and a second valve opening 31f, which will be described later. First, the connecting passage 31 between the first chamber oil passage 32 and the bottom portion 30a will be referred to as a "connecting passage inlet portion 31a" below.

The valve portion 28 of the solenoid valve 13 includes a generally cylindrical valve body 39 , a spool 40 slidably disposed within the valve body 39 , and a retainer 41 fixed to the inner peripheral portion of the valve body 39 . , and a second coil spring 64 which is a biasing member arranged between the retainer 41 and the spool 40 with a predetermined set load W2 applied thereto.

The valve body 39 has a spool accommodating portion 39a that slidably accommodates the spool 40. The spool accommodating portion 39a includes a large-diameter tubular portion 39b located on the side of the connection passage inlet portion 31a, and a large-diameter tubular portion 39b. A small-diameter tubular portion 39c formed integrally with the shaped portion 39b and having an inner diameter smaller than that of the large-diameter tubular portion 39b.

On the inner peripheral surface near one end of the large-diameter cylindrical portion 39b, a disk-shaped metal fixing member is axially opposed to the bottom portion 30a of the control valve housing portion 30, to which the connection passage inlet portion 31a opens. A retainer 41 forming a part is press-fitted and fixed. The retainer 41 forms, between itself and the bottom portion 30a of the control valve housing portion 30, a tip side passage 31b into which oil is introduced via a connection passage inlet portion 31a. A surface 41 a of the retainer 41 facing the second coil spring 64 is a surface against which one axial end of the second coil spring 64 elastically abuts.

As shown in FIGS. 4(a) and 4(b), two flat portions 39d formed in a width across flat shape are formed on the outer peripheral portion of the large-diameter tubular portion 39b at positions facing each other in the radial direction. formed. A concave portion 39f is formed between the flat portion 39d and a stepped portion 39e provided on one axial end side of the outer peripheral portion of the small-diameter cylindrical portion 39c, and the concave portion 39f is connected to the tip-side passage 31b. , an axial passage 31c is formed through which the oil from the tip side passage 31b flows in the axial direction of the valve body 39. As shown in FIG. At a position near the stepped portion 39e of each flat portion 39d, a first valve opening 31d is formed that penetrates the inner peripheral surfaces of the flat portion 39d and the large-diameter cylindrical portion 39b and communicates with the axial passage 31c. . The first valve opening 31d always communicates with an introduction passage 31e provided around an intermediate shaft portion 40b of the spool 40, which will be described later.

Four second valve openings 31f are formed in the small-diameter tubular portion 39c at positions near the stepped portion 39e so as to penetrate the inner and outer peripheral surfaces of the small-diameter tubular portion 39c. The second valve openings 31f are provided at equidistant positions in the valve body 39 in the circumferential direction. One of the four second valve openings 31f faces the second chamber oil passage 34 formed in the block portion 1k. Further, four third valve openings 62 are formed through the inner and outer peripheral surfaces of the small-diameter tubular portion 39c at positions near the solenoid portion 29 in the small-diameter tubular portion 39c. The third valve openings 62 are provided at equal intervals in the circumferential direction of the valve body 39 and face an external connection passage 63 provided near the control valve housing port 30b of the control valve housing portion 30 . The external connection path 63 communicates with the outside having a lower pressure than the pressure of the oil discharged from the discharge port 24, such as an oil pan (not shown).

An annular groove 39g is formed on the outer peripheral surface of the small-diameter cylindrical portion 39c at a position between the second valve opening 31f and the third valve opening 62, in which the first seal ring 42, which is an O-ring, is fitted. there is The first seal ring 42 liquid-tightly seals between the inner peripheral surface of the control valve accommodating portion 30 and the outer peripheral surface of the small-diameter cylindrical portion 39c.

The spool 40 includes a large diameter portion 40a, an intermediate shaft portion 40b integrally formed with the large diameter portion 40a, and an intermediate shaft portion 40b integrally formed with the intermediate shaft portion 40b. It has a medium-diameter portion 40c larger in diameter than the portion 40b and a rear end shaft portion 40d integrally formed with the medium-diameter portion 40c. The spool 40 is arranged such that the large diameter portion 40a is positioned on the connection path inlet portion 31a side as shown in FIG. 4(a).

The large diameter portion 40 a slides on the inner peripheral surface of the valve body 39 between the first valve opening 31 d and the retainer 41 . A circular recessed groove portion 40e for accommodating a portion of the second coil spring 64 on the other axial end side is formed in one axial end surface 40n of the large diameter portion 40a. A spring accommodating portion 65 that accommodates the second coil spring 64 is provided between the bottom surface 40 f of the circular groove portion 40 e and the retainer 41 . A bottom surface 40f of the circular groove portion 40e is a surface with which the other axial end portion of the second coil spring 64 is elastically abutted. A drain connection passage 40g is formed in the center of the bottom surface 40f of the circular recessed groove 40e and extends axially from the bottom surface 40f beyond the middle diameter portion 40c to a position just before the center of the rear end shaft portion 40d. A rectangular spool drain hole 40h is formed radially through the end portion of the drain connection passage 40g, that is, the end portion located on the rear end shaft portion 40d side. The spool drain holes 40h are provided at two positions facing each other in the radial direction, and communicate with the outside through holes (not shown) provided in the block portion 1k. During operation of the internal combustion engine, if the temperature of the air in the spring accommodating portion 65 rises and the air expands, the expanded air is discharged to the outside through the drain connection passage 40g, the spool drain hole 40h and the hole. discharged to

The other axial end face of the large-diameter portion 40a is formed into an annular first wall on which the main gallery pressure P introduced via the connecting passage inlet portion 31a, the tip side passage 31b, the axial passage 31c, and the first valve opening 31d acts. 1 pressure receiving surface portion 40i.

The intermediate shaft portion 40b is provided integrally with the other end in the axial direction of the large diameter portion 40a. An introduction passage 31e is formed that communicates with the axial passage 31c.

The medium diameter portion 40c is provided integrally with the other axial end of the intermediate shaft portion 40b so as to axially face the large diameter portion 40a with the intermediate shaft portion 40b interposed therebetween. side slides against the inner peripheral surface of the small-diameter cylindrical portion 39c. One axial end surface of the intermediate diameter portion 40c is formed in a ring-shaped second pressure receiving area on which the main gallery pressure P introduced through the connecting passage inlet portion 31a, the tip side passage 31b, the axial passage 31c, and the first valve opening 31d acts. It becomes the surface part 40j. The second pressure receiving surface portion 40j is set smaller than the first pressure receiving surface portion 40i. By multiplying the main gallery pressure P by the difference in pressure receiving surface area between the first pressure receiving surface portion 40i of the large diameter portion 40a and the second pressure receiving surface portion 40j of the medium diameter portion 40c, the spool 40 is moved toward the tip portion side of the valve body 39. An urging hydraulic pressure Fp is calculated.

The rear end shaft portion 40d is provided integrally with the other end in the axial direction of the intermediate diameter portion 40c, and the axial end face 40k can come into contact with a rod 50 of the solenoid portion 29, which will be described later.

The solenoid portion 29 is provided at the rear end portion of the valve body 39 and includes a case 43 , a closing member 44 , a coil 45 , a bobbin 46 , a fixed iron core 47 , a solenoid portion sleeve 48 , and a movable iron core 49 . and a rod 50.

The case 43 is formed in a cylindrical shape and accommodates the coil 45, the bobbin 46, the fixed iron core 47, the solenoid section sleeve 48, the movable iron core 49 and the rod 50 inside. The case 43 is closed by a bottomed cylindrical closing member 44 .

The coil 45 is wound around a generally cylindrical bobbin 46 . A substantially cylindrical sleeve for solenoid portion 48 is press-fitted and fixed to the inner peripheral surface of the bobbin 46 on the one axial end 46a side. A movable iron core 49 is provided on the inner peripheral side of the solenoid portion sleeve 48 so as to be movable along the axial direction. A substantially cylindrical stationary core 47 is press-fitted to the inner peripheral surface of the bobbin 46 on the side of the other end 46 b in the axial direction. A rod 50 is provided on the inner peripheral side of the fixed iron core 47 and is movable in the axial direction by operating integrally with the movable iron core 49 as the movable iron core 49 moves. The tip portion 50a of the rod 50 can bias the axial end surface 40k of the rear end shaft portion 40d of the spool 40 accommodated in the valve body 39 as the rod 50 moves toward one end in the axial direction. there is Further, the space between the fixed iron core 47 and the valve body 39 is liquid-tightly sealed by an annular seal member, for example, a second seal ring 51 which is an O-ring. Similarly, the space between the fixed core 47 and the bobbin 46 is liquid-tightly sealed by an annular seal member, for example, a third seal ring 52 which is an O-ring.

In the electromagnetic valve 13, the solenoid portion 29 urges the rear end shaft portion 40d of the spool 40 from the rear end portion of the valve body 39 toward the tip portion in response to an externally applied electric signal. More specifically, when a pulse voltage is applied to the coil 45 from an electronic controller (not shown), the solenoid portion 29 applies a thrust force to the movable iron core 49 according to the voltage value of the pulse voltage. Then, the spool 40 is set by combining the resultant force Fp+Fr of the hydraulic force Fp applied to the spool 40 and the thrust of the movable iron core 49 (the pressing force Fr of the rod 50) transmitted through the rod 50 and the spring force Fs2 of the second coil spring 64. It is designed to move forward and backward based on the relative difference.

The electronic controller employs a so-called PWM (Pulse Width Modulation) method, and modulates the pulse width of the pulse voltage applied to the coil 45. That is, by changing the duty ratio D, the pulse voltage applied to the coil 45 The voltage value is controlled steplessly. In addition, the electronic controller detects the operating state of the engine from the oil temperature, water temperature, engine speed, load, etc., and energizes the coil 45 especially when the engine is in a low speed state such as when the engine is started. On the other hand, when the engine speed N exceeds a predetermined value, the coil 45 is energized in order to adjust the main gallery pressure P.

FIG. 5 is a cross-sectional view of the variable displacement oil pump showing the first state of the solenoid valve 13, and FIG. 6 is a cross-sectional view of the variable displacement oil pump showing the second state of the solenoid valve 13. 5 and 6 show the axial position of the spool and the flow of oil through the solenoid valve 13, the solenoid valve 13 is arranged on the side of the cam ring 6. The electromagnetic valve 13 has the positional relationship shown in FIGS. 1 to 3 as described above. FIG. 7 is a characteristic diagram showing the correlation between the engine speed N and the main gallery pressure P of the variable displacement oil pump of the first embodiment.

The operation of the solenoid valve 13 and the associated operation of the cam ring 6 will be described below.

First, when the coil 45 of the solenoid valve 13 is not energized, that is, when the duty ratio D is 0%, the spool 40 is subjected to the hydraulic pressure Fp acting on the spool 40 and the spring force Fs2 of the second coil spring 64. moves axially within the valve body 39 based on . More specifically, when the hydraulic force Fp is greater than the spring force Fs, the spool 40 moves toward the distal end of the valve body 39. On the other hand, when the spring force Fs2 is greater than the hydraulic force Fp, The spool 40 moves toward the rear end of the valve body 39 .

As shown in FIG. 7, when the engine speed N is equal to or less than the predetermined engine speed N2, the main gallery pressure P is equal to or less than the predetermined value P2. Here, the predetermined value P2 indicates the required engine oil pressure required for lubricating the bearings of the crankshaft when the engine is rotating at high speed. Further, the hydraulic pressure Fp, which is proportional to the main gallery pressure P, is equal to or less than a predetermined value, and the hydraulic pressure Fp becomes equal to or less than the spring force Fs2. Therefore, the spool 40 is at a position near the solenoid portion 29 (the position of the spool 40 shown in FIG. 5). At this time, the communication between the second valve opening 31f and the external connection passage 63 is blocked by the outer peripheral surface of the intermediate diameter portion 40c, and the first valve opening 31d and the second valve opening 31f communicate through the introduction passage 31e. As a result, as shown in FIG. 5, the oil in the main gallery flows through the first chamber oil passage 32, the connection passage inlet portion 31a, the tip side passage 31b, the axial direction passage 31c, the first valve opening 31d, the introduction passage 31e, It is led to the second chamber 27 via the second valve opening 31 f and the second chamber oil passage 34 . A resultant force PO2+Fs1 of the internal pressure PO2 of the second chamber 27 and the spring force Fs1 of the first coil spring exceeds the internal pressure PO1 of the first chamber . Therefore, the cam ring 6 is at the most eccentric position (the position of the cam ring 6 shown in FIG. 5), and the amount of eccentricity is maximized. At this time, the solenoid valve 13 connects the tip side passage 31b and the second chamber 27 via the axial passage 31c, the first valve opening 31d, the introduction passage 31e, the second valve opening 31f, and the second chamber oil passage 34. It is in the first state. Therefore, as shown in FIG. 7, when the engine speed N is equal to or lower than the predetermined engine speed N2, the main gallery pressure P changes according to the engine speed N at its maximum capacity.

Further, when the engine speed N is higher than the predetermined engine speed N2, when the main gallery pressure P reaches a predetermined value P2, the hydraulic pressure Fp reaches a predetermined value and becomes larger than the spring force Fs2. . Then, the spool 40 slightly moves toward the distal end of the valve body 39 by a predetermined distance (the position of the spool 40 shown in FIG. 6). During this movement, since the duty ratio D is 0%, the rod 50 is at the most retracted position and is separated from the other end of the spool 40 in the axial direction. The second valve opening 31f communicates with the external connection passage 63, and the oil in the second chamber 27 flows through the second chamber oil passage 34, the second valve opening 31f, the discharge passage 60, and the third valve opening 62. and discharged to the outside through the external connection path 63 . At this time, the electromagnetic valve 13 is in the second state in which the second chamber 27 and the external connection passage 63 are connected via the second chamber oil passage 34, the second valve opening 31f, the discharge passage 60, and the third valve opening 62. be. As a result, the internal pressure PO1 in the first chamber 26 becomes high, and this internal pressure PO1 urges the cam ring 6 toward the first coil spring 7 against the spring force Fs1 of the first coil spring 7 . Then, the cam ring 6 moves toward the first coil spring 7 and the eccentricity is reduced. Accordingly, the discharge amount of the variable displacement pump decreases, and the main gallery pressure P decreases toward the predetermined value P2. Further, when the main gallery pressure P falls below the predetermined value P2, the hydraulic pressure in the first chamber 26 becomes low again, the cam ring 6 moves to the position on the first chamber 26 side, and the capacity increases.

In this way, when the main gallery pressure P is lower than the predetermined value P2, the spool 40 is positioned closer to the solenoid portion 29 and allows communication between the main gallery and the second chamber 27, while the main gallery pressure P decreases to the predetermined value P2. , the spool 40 is at a position separated from the solenoid portion 29, and the second chamber 27 and the outside are communicated. As a result, the main gallery pressure P is maintained at the predetermined value P2 and within a range (control oil pressure Pt2) near the predetermined value P2.

Further, when the coil 45 of the solenoid valve 13 is energized, that is, when the duty ratio D is X (0<X<100)%, the spool 40 changes the hydraulic pressure Fp applied to the spool 40 and the force of the rod 50. It moves in the axial direction within the valve body 39 based on the resultant force Fp+Fr with the pressing force Fr and the spring force Fs2 of the second coil spring 64 . More specifically, when the resultant force Fp+Fr is greater than the spring force Fs2, the spool 40 moves toward the distal end of the valve body 39. On the other hand, when the spring force Fs2 is greater than the resultant force Fp+Fr, the spool 40 , moves to the rear end side of the valve body 39 . When the valve body 39 moves toward one end, the pressing force Fr assists the hydraulic force Fp, so the main gallery pressure P moves the spool 40 with a predetermined pressure Px lower than the predetermined value P2. Along with this, the control oil pressure controlled by the spool 40 also becomes a predetermined control oil pressure Ptx lower than the control oil pressure Pt2. Further, when the duty ratio D is the maximum value, that is, 100%, the control oil pressure Pt1 controlled by the spool 40 is maintained at the lowest oil pressure P1 or in a range near P1.

When the engine is in a low rotation state such as when the engine is started, that is, when the engine speed N is lower than N1, the coil 45 is de-energized and the duty ratio D is 0%.

[Effect of the first embodiment]
In the conventional variable displacement oil pump, in order to form an oil passage leading the oil from the main gallery to the first chamber and to the second chamber via the solenoid valve, the mating surfaces of the housing body and the cover member are formed. The discharge port was bypassed by utilizing and in some cases forming a lateral hole. Therefore, there is a problem that the oil passage becomes relatively long and complicated, making it difficult to form the oil passage.
In addition, there are problems such as an increase in the size of the variable displacement oil pump, a decrease in the sealing performance of the mating surface between the housing body and the cover member, and a decrease in the responsiveness of the hydraulic pressure between the second chamber and the solenoid valve. rice field.

In the first embodiment, the variable displacement oil pump is linearly formed at a position adjacent to the first chamber 26 and the second chamber 27 when viewed along the rotation axis O1 of the pump structure. A connecting passage 31, a first chamber oil passage 32 branched in a direction intersecting the longitudinal direction of the connecting passage 31 and connected to the first chamber 26, and a control valve accommodating portion 30 intersecting the longitudinal direction of the connecting passage 31. and a second chamber oil passage 34 branched in the direction and connected to the second chamber 27 . An electromagnetic valve 13 forming a part of the connection passage 31 is inserted into the control valve accommodating portion 30 . ing.

Therefore, the solenoid valve 13 itself is directly connected to the first chamber oil passage 32 and the second chamber oil passage 34, which are the only lateral holes, and the oil passages are provided in the valve portion 28 of the solenoid valve 13 and its outer peripheral portion. is sealed by a sealed ring 42. Therefore, since a relatively long seal by the mating surfaces between the housing body 1 and the cover member 2 is not required, an oil passage for guiding oil from the main gallery to the first chamber 26 and the second chamber 27 can be easily formed. can do. Also, deterioration of the sealing performance between the solenoid valve 13 and the first and

second chambers

26 and 27 can be suppressed. In addition, since the oil passage is shortened, the variable displacement oil pump can be downsized and the manufacturing cost of the pump can be reduced.

Further, in the configuration of the variable displacement oil pump of the first embodiment, the solenoid valve 13 is arranged at a position close to the second chamber 27, and the oil from the main gallery flows through the straight connecting passage 31 and the second chamber. Since the oil is guided to the second chamber 27 via a relatively short oil passage including the oil passage 34, the responsiveness of hydraulic pressure to the second chamber 27 can be improved. When discharging oil from the second chamber 27 to the outside, the oil can be discharged through the second chamber oil passage 34 and the solenoid valve 13, so even in such a case, the response of the hydraulic pressure can be improved. can be improved.

Furthermore, in the first embodiment, the solenoid valve 13 is switched between the first state in which the distal end side passage 31b and the second chamber 27 are connected and the second state in which the second chamber 27 and the external connection path 63 are connected. configured to be switchable.

Therefore, oil is appropriately supplied to the second chamber 27 in the first state, while oil is appropriately discharged from the second chamber 27 in the second state. Therefore, the variable displacement oil pump can be controlled to a predetermined oil pressure.

In the first embodiment, the valve portion 28 of the solenoid valve 13 is fixed to the valve body 39, the spool 40 slidably arranged in the valve body 39, and the inner peripheral portion of the valve body 39. and a second coil spring 64 arranged between the retainer 41 and the spool 40 .

A solenoid valve used in a valve timing control device for an internal combustion engine generally has a valve body, a spool, a valve sleeve, and a coil spring. However, in this embodiment, the disk-shaped retainer 41, which is a smaller component, is used in place of the cylindrical valve sleeve, which simplifies the structure of the solenoid valve 13 and reduces the manufacturing cost of the solenoid valve 13. can be reduced.

Further, in the first embodiment, the oil from the main gallery is introduced into the tip side passage 31b and flows radially through the valve body 39, then axially through the axial passage 31c, and then flows through the first valve. It is introduced into the introduction passage 31e through the opening 31d.

If oil is introduced from the tip side passage and hydraulic pressure is directly applied to the spool, there is a risk that the spool will be affected by the axial hydraulic pressure and its stable operation will be suppressed. However, as in the first embodiment, the spool 40 is stably operated by bypassing the hydraulic pressure from the radially outer side of the valve body 39 instead of directly acting in the axial direction of the spool 40, and the solenoid valve 13 is operated. You can have more control.

Further, in the first embodiment, the solenoid valve 13 is attached to the rear end of the valve body 39 in response to an electric signal externally applied to the rear end of the spool 40 from the rear end of the valve body 39 toward the front end thereof. It has a solenoid portion 29 that biases the shaft portion 40d.

Therefore, by appropriately controlling the duty ratio D to adjust the hydraulic pressure of the second chamber 27, the hydraulic pressure of the variable displacement oil pump can be controlled steplessly.

Furthermore, in the first embodiment, the spool 40 includes a spool drain hole 40h that opens in the rear end shaft portion 40d in the radial direction, and a drain connection passage that connects the spool drain hole 40h and the inside of the second coil spring 64. 40 g.

Therefore, the air expanded in the spring accommodating portion 65 during operation of the internal combustion engine is discharged to the outside through the drain connection passage 40g and the spool drain hole 40h. As a result, expansion and contraction of the second coil spring 64 are not suppressed by the expanded air, and the electromagnetic valve 13 is efficiently operated only by the hydraulic force Fp, the pressing force Fr of the rod 50, and the spring force Fs2 of the second coil spring 64. can be activated.

Also, in the first embodiment, the volume of the second chamber 27 increases when the cam ring 6 moves in the direction in which the flow rate of the oil discharged from the discharge port 24 increases.

When the second chamber 27 is configured in this way, the spring force of the first coil spring 7 acts in the same direction as the hydraulic pressure in the second chamber 27 biases the cam ring 6 . Therefore, by increasing the contribution of the hydraulic pressure to the operation of the cam ring 6, the size of the first coil spring 7 can be reduced and the variable displacement oil pump can be simplified.

In addition, by controlling the movement of the cam ring 6 mainly by the hydraulic pressure in the second chamber 27 using the small first coil spring 7, the minimum discharge pressure of the variable displacement oil pump is set low, and the fuel of the internal combustion engine is reduced. Consumption rate can be improved.

Furthermore, in the first embodiment, the solenoid valve 13 has a tip portion of the valve portion 28 that is located between the first chamber 26 and the second chamber 27 when viewed in the direction along the rotation axis O1 of the pump structure. A solenoid portion 29 is provided outside the second chamber 27 so as to overlap a part of the cam ring 6 provided therebetween and on the opposite side of the tip portion of the valve portion 28 .

With this arrangement of the solenoid valve 13 and the cam ring 6 , the distance between the solenoid valve 13 and the second chamber 27 is shorter than when the solenoid valve 13 is arranged on the side of the cam ring 6 . Therefore, when supplying oil to the second chamber 27 and when discharging oil from the second chamber 27, the responsiveness of the hydraulic pressure can be improved.

Further, in the first embodiment, the connection path 31 is arranged between the pivot pin 22 of the cam ring 6 and the drive shaft 3 of the pump assembly when viewed in the direction along the rotation axis O1 of the pump assembly. It is

Therefore, compared to the case where the connection path 31 is arranged on the opposite side of the pivot pin 22 with the drive shaft 3 interposed therebetween, the connection path 31 and the first and

second chambers

26 and 27 are arranged in the first and second chambers. They are connected over a short distance via

paths

32 and 34, so that the supply of oil to the first chamber 26 and the supply and discharge of oil to and from the second chamber 27 can be performed quickly.

Furthermore, in the first embodiment, the first chamber oil passage 32 extends radially from the first chamber 26 toward the pivot pin 22 of the cam ring 6 when viewed in the direction along the rotation axis O1 of the pump assembly. , that is, it opens on the swing fulcrum side, and when viewed along the rotation axis O1 of the pump structure, the second chamber oil passage 34 extends radially from the second chamber 27 at the swing fulcrum of the cam ring 6 . open on the side. At this time, the connection path 31 is formed at a position that connects the first chamber 26 and the second chamber 27 at the shortest distance when viewed from the direction along the rotation axis O1 of the pump assembly.

Therefore, the connection path 31 and the first and

second chambers

26, 27 are connected at the shortest distance via the first and second

chamber oil paths

32, 34, so that oil is supplied to the first chamber 26 and the second chamber 26 is supplied. Oil can be supplied and discharged from the chamber 27 more quickly.

Further, in the first embodiment, an introduction port 33 through which oil from the main gallery is introduced is provided between the first chamber 26 and the connection path 31 .

Therefore, the distance between the introduction port 33 and the first chamber 26 can be shortened compared to the case where the introduction port 33 is provided in the connection path 31, and the oil can be efficiently supplied to the first chamber 26. .

[Second embodiment]
FIG. 8 is a cross-sectional view of the solenoid valve 13 of the second embodiment.

In the second embodiment, unlike the first embodiment, the solenoid valve 13 has the same configuration as a solenoid valve of the type generally used in a valve timing control device for an internal combustion engine, and the valve portion 28 is a valve It has a part sleeve 53 .

The valve portion 28 includes a cylindrical valve body 39, a cylindrical valve portion sleeve 53 fixed to the inner periphery of the distal end portion of the valve body 39, and a valve portion disposed in the valve body 39. A spool 40 slidably provided on the inner peripheral surface of the body 39 and the outer peripheral surface of the valve sleeve 53, and a second coil spring 64 provided between the spool 40 and the valve sleeve 53. , is equipped with

The valve body 39 has a hole portion 39j, four second chamber openings 39k, an external connection path 63, and four air drain holes 39m.

The hole 39j is open at the tip 39h and extends from the tip 39h toward the rear end 39i. The hole 39j opens to a connection path entrance (not shown) provided in the housing body. The inner peripheral surface of the hole 39j is formed with an annular recess 39f into which the outer peripheral portion of the retaining ring 54 used for fixing the valve sleeve 53 is fitted.

The second chamber openings 39k are provided at equal intervals in the circumferential direction on the rear end portion 39i side of the valve body 39, and penetrate the valve body 39 in the radial direction. The second chamber opening 39k communicates with a second chamber oil passage (not shown) connected to the second chamber of the variable displacement oil pump.

The external connection path 63 radially penetrates the valve body 39 between the second chamber opening 39k and the rear end portion 39i. The external connection path 63 communicates with the outside having a lower pressure than the pressure of the oil discharged from the discharge port 24, such as an oil pan.

The air drain holes 39m are provided at circumferentially equal intervals in the vicinity of the tip portion 39h, and penetrate the valve body 39 in the radial direction. The air drain hole 39m communicates between the spring accommodating portion 65 that accommodates the second coil spring 64 and the outside.

The valve portion sleeve 53 has a cylindrical body portion 53a and an annular flange portion 53b protruding radially outward from the outer circumference of one axial end portion of the body portion 53a.

The main body portion 53a includes a sleeve axial opening 53c facing the hole portion 39j, and four sleeve axial openings 53c provided on the rear end portion 39i side of the sleeve axial opening 53c and penetrating in the radial direction at equally spaced positions in the circumferential direction. It has an opening 53d. Oil from the inside of the body portion 53a is led to the sleeve radial opening 53d.

The flange portion 53b is fixed to the stepped portion 39e by being pressed toward the rear end portion 39i by the retaining ring 54 while being in contact with the stepped portion 39e provided in the hole portion 39j of the valve body 39. As shown in FIG. 8, when the flange portion 53b is fixed to the stepped portion 39e, the main body portion 53a extends along the axis of the valve body 39 from the joint portion with the flange portion 53b to the axial position corresponding to the second chamber opening 39k. extending along the direction. A surface 53e of the flange portion 53b adjacent to the body portion 53a is a surface with which one end portion of the second coil spring 64 is elastically abutted.

The spool 40 has a large diameter portion 40a, an intermediate shaft portion 40b, a medium diameter portion 40c, and a rear end shaft portion 40d. As shown in FIG. 8, inside the large-diameter portion 40a, the intermediate shaft portion 40b and the medium-diameter portion 40c, a central hole portion 39n extending from one axial end of the large-diameter portion 40a to the other axial end of the medium-diameter portion 40c is provided. is formed. The hole diameter of the central hole portion 39n is set to a size corresponding to the outer diameter of the valve sleeve 53, so that the inner peripheral surface of the central hole portion 39n is aligned with the outer peripheral surface of the valve sleeve 53. It is slidable against.

The large diameter portion 40a is provided between the sleeve axial opening 53c and the sleeve radial opening 53d so as to extend from the front end portion 39h side of the valve body 39 toward the rear end portion 39i side.

The intermediate shaft portion 40b has a spool radial opening 40m provided at a position axially adjacent to the large diameter portion 40a. The spool radial opening 40m opens into the central hole portion 39n of the intermediate shaft portion 40b and communicates with the sleeve radial opening 53d of the valve portion sleeve 53 . Oil that has passed through the body portion 53a and the sleeve radial opening 53d is led to the spool radial opening 40m. The oil guided to the spool radial opening 40m is guided to the second chamber (not shown) through the introduction passage 31e, the second chamber opening 39k and the second chamber oil passage (not shown).

The medium diameter portion 40c is arranged between the external connection path 63 and the second chamber opening 39k when the second coil spring 64 is expanded as shown in FIG.

The second coil spring 64 urges the spool 40 toward the rear end portion 39i of the valve body 39 so that the one axial end surface 40n of the large diameter portion 40a and the surface 53e of the flange portion 53b of the valve portion sleeve 53 are connected to each other. is placed in a compressed state between

[Effect of Second Embodiment]
In the second embodiment, the valve portion 28 of the solenoid valve 13 includes a valve body 39, a valve portion sleeve 53 fixed to the inner periphery of the valve body 39, an inner peripheral surface of the valve body 39 and a valve portion sleeve 53 fixed to the inner periphery of the valve body 39. A spool 40 slidably provided on the outer peripheral surface of the sleeve 53, and a second coil spring (spool biasing member) 64 provided between the spool 40 and the valve portion sleeve 53. there is

Therefore, by providing a sleeve radial opening 53d in the main body portion 53a of the valve sleeve 53 and appropriately communicating with the second chamber opening 39k, the hydraulic pressure introduced into the second chamber 27 can be more finely controlled. .

Further, in the second embodiment, the solenoid valve 13 rotates the spool 40 from the rear end portion 39i of the valve body 39 toward the front end portion 39h in response to an electric signal externally applied to the rear end portion 39i of the valve body 39 . has a solenoid portion 29 for biasing the rear end shaft portion 40d.

Therefore, even in the solenoid valve 13 of the second embodiment having the valve portion sleeve 53, by appropriately controlling the duty ratio D to adjust the hydraulic pressure in the second chamber, the hydraulic pressure of the variable displacement oil pump is nullified. It can be controlled in stages.

[Third embodiment]
9 is a front view of the variable displacement oil pump of the third embodiment showing the non-operating state of the solenoid valve 13, and FIG. 10 is a variable displacement oil pump of the third embodiment showing the operating state of the solenoid valve 13. 1 is a front view of a type oil pump. FIG. In FIGS. 9 and 10, the solenoid valve 13 is shown to be arranged radially outward of the cam ring 6 in order to facilitate understanding of the oil flow. The valve portion 28 of the electromagnetic valve 13 is arranged so as to face a partial region of the cam ring 6 when viewed in the direction along O1.

In the third embodiment, the cam ring 6 does not swing around the pivot pin but moves linearly, so that the pump assembly is aligned with the center of the inner circumference of the cam ring 6 and the drive shaft 3 of the pump assembly. It is arranged so that the rotation axis O1 is eccentric.

The cam ring 6 includes a first projecting portion 55 projecting radially outward from the outer peripheral portion of the cam ring 6 and a second projecting portion 55 provided radially opposite to the first projecting portion 55 and projecting from the outer peripheral portion of the cam ring 6 . and a protrusion 56 .

The first protrusion 55 is slidably arranged between two

side walls

57a, 57a of a first recess 57 provided in the inner peripheral wall of the pump housing chamber 1a. Here, the sliding direction of the first projecting portion 55 is the direction along the longitudinal direction of the electromagnetic valve 13 . A first chamber 26 into which oil from the main gallery is introduced is formed between the tip of the first protrusion 55 and the bottom of the first recess 57 .

The second projecting portion 56 is slidably disposed between two

side walls

58a, 58a of a second recessed portion 58 provided in the inner peripheral wall of the pump housing chamber 1a. Here, the sliding direction of the second projecting portion 56 is along the longitudinal direction of the electromagnetic valve 13 as with the first projecting portion 55 . Between the second protrusion 56 and the bottom of the second recess 58 is a second chamber 27 into which oil from the main gallery can be introduced via the solenoid valve 13 .

A third coil spring 59 that is compressed by a predetermined set load W3 is provided between the second projection 56 and the bottom of the second recess 58 . The third coil spring 59 moves the cam ring 6 linearly toward the first chamber 26 against the hydraulic pressure in the first chamber 26 by the combined force of the biasing force of the third coil spring 59 and the hydraulic pressure in the second chamber 27 . Let

As shown in FIG. 9, when the solenoid valve 13 is in a non-operating state, the oil in the main gallery flows through the first chamber oil passage 32, the connecting passage inlet 31a, the tip side passage 31b, the axial passage 31c, and the first valve. The oil is led to the introduction passage 31e through the opening 31d, and then to the second chamber 27 through the second valve opening 31f and the second chamber oil passage 34 from the introduction passage 31e.

Further, as shown in FIG. 10, when the solenoid valve 13 is in the operating state, the oil in the main gallery flows through the first chamber oil passage 32, the connection passage inlet portion 31a, the tip side passage 31b, the axial direction passage 31c and the first oil passage. It is led to the introduction passage 31e through the valve opening 31d. At the same time, the oil in the second chamber 27 is discharged to the outside through the second chamber oil passage 34, the second valve opening 31f, the discharge passage 60, the third valve opening 62 and the external connection passage 63.

[Effect of the third embodiment]
In the third embodiment, in the variable displacement oil pump, the cam ring 6 does not swing around the pivot pin but moves linearly.

Even with the variable displacement oil pump having such a configuration, an oil passage for guiding oil from the main gallery to the first chamber 26 and the second chamber 27 can be easily formed as in the first embodiment. , it is possible to suppress the deterioration of the sealing performance. In addition, the variable displacement oil pump can be made smaller and manufacturing costs associated with the pump can be reduced.

[Fourth embodiment]
11 is a front view of the variable displacement oil pump of the fourth embodiment showing the non-operating state of the solenoid valve 13, and FIG. 12 shows the operating state of the solenoid valve 13 of the variable displacement oil pump of the fourth embodiment. 1 is a front view of a type oil pump. FIG. In FIGS. 11 and 12, the solenoid valve 13 is shown to be disposed radially outward of the cam ring 6 in order to facilitate understanding of the oil flow. The valve portion 28 of the electromagnetic valve 13 is arranged so as to face a partial region of the cam ring 6 when viewed in the direction along O1.

In the variable displacement oil pump of the fourth embodiment, unlike the first embodiment, the second chamber 27 is arranged above the cam ring reference line M and adjacent to the first chamber 26 in the circumferential direction. are arranged to More specifically, as shown in FIGS. 11 and 12, only the first and

second seal members

16, 18 are present as seal members, and both the first and

second seal members

16, 18 are aligned with the cam ring reference line M is placed above. A first chamber 26 is formed between the pivot pin 22 and the first seal member 16 , and a second chamber 27 is formed between the first seal member 16 and the second seal member 18 . The second chamber 27 is configured such that its volume increases when the cam ring 6 moves in a direction in which the flow rate of oil discharged from the discharge port 24 decreases.

Further, the spool 40 of the solenoid valve 13 has an annular rear end shaft enlarged diameter portion 40o provided at the other axial end of the rear end shaft portion 40d of the spool 40. As shown in FIG. The rear end shaft portion enlarged diameter portion 40o is provided at a position facing the intermediate diameter portion 40c and the spool 40 in the axial direction, and has the same outer diameter as the outer diameter of the intermediate diameter portion 40c.

As shown in FIG. 11, when the solenoid valve 13 is in a non-operating state, the oil in the main gallery flows through the first chamber oil passage 32, the connecting passage inlet 31a, the tip side passage 31b, the axial passage 31c, and the first valve. It is led to the introduction passage 31e through the opening 31d. At the same time, the oil in the second chamber 27 is discharged to the outside through the second chamber oil passage 34, the second valve opening 31f, the discharge passage 60, the third valve opening 62 and the external connection passage 63.

Further, as shown in FIG. 12, when the solenoid valve 13 is in the operating state, the oil in the main gallery flows through the first chamber oil passage 32, the connecting passage inlet 31a, the tip side passage 31b, the axial passage 31c, the first It is led to the second chamber 27 via the valve opening 31d, the discharge passage 60, the second valve opening 31f, and the second chamber oil passage .

[Effect of the fourth embodiment]
In the fourth embodiment, the second chamber 27 is arranged above the cam ring reference line M and adjacent to the first chamber 26 in the circumferential direction.

In each of the above embodiments, an example in which the variable displacement oil pump has the first chamber 26 and the second chamber 27 is disclosed. However, by arranging the solenoid valve near the first chamber, the solenoid valve seals the oil passage in the first chamber, and there is no need to bypass the oil passage.

Claims

a housing having a pump chamber;
an adjustment member movably provided inside the pump housing chamber;
A pump structure provided in the adjustment member, which is driven to rotate and discharges oil sucked from a suction part from a discharge part, and when the adjustment member moves, the oil is discharged from the discharge part. the pump arrangement that varies the flow rate of
A flow rate of oil discharged from the discharge portion is formed between the pump housing chamber and the adjustment member in a radial direction with respect to the rotation axis of the pump structure, and the oil discharged from the discharge portion is guided. a first chamber whose volume increases when the adjustment member moves in a direction in which the
a second chamber formed between the pump accommodating chamber and the adjustment member in a radial direction with respect to the rotation axis of the pump structure, and into which the oil discharged from the discharge portion is guided;
A connection path formed linearly adjacent to the first chamber and the second chamber when viewed from the direction along the rotation axis of the pump assembly, and through which the oil that has passed through the main gallery is guided. and,
a first chamber oil passage branched in a direction crossing the longitudinal direction of the connection passage and connected to the first chamber;
A control valve housing portion connected to the connection path and formed to have a diameter larger than that of the connection path, the control valve housing portion having a bottom opening to the connection path, a control valve housing opening facing the bottom portion, and the control valve housing portion having an external connection passage that communicates with the outside having a lower pressure than the pressure of the oil discharged from the discharge portion;
a second chamber oil passage branching from the control valve accommodating portion in a direction crossing the longitudinal direction of the connection passage and connected to the second chamber;
A control valve inserted into the control valve housing portion from the control valve housing opening of the control valve housing portion toward the bottom portion, wherein the control valve housing portion has a bottom portion and a tip end portion of the control valve. the control valve that connects the second chamber oil passage to the tip side passage that is formed;
Variable displacement oil pump with
In the variable displacement oil pump according to claim 1,
A variable displacement oil pump characterized by switching between a first state in which the tip side passage and the second chamber are connected and a second state in which the second chamber and the external connection path are connected.
In the variable displacement oil pump according to claim 1,
The control valve is
a fixing portion provided at a position facing the bottom portion of the control valve housing portion where the connection path opens, and forming the tip side passage between the bottom portion of the control valve housing portion;
A cylindrical valve body that is housed in the control valve housing portion and that has the fixing portion fixed to the inner peripheral surface thereof, wherein the distal end side is provided between the inner circumference of the control valve housing portion and the outer circumference of the fixing portion. a recess communicating with the passageway to form an axial passage; a first valve opening provided in the recess and penetrating the outer and inner peripheries of the valve body; the valve body having a second valve opening provided on the rear end side, penetrating the outer and inner circumferences of the valve body and facing the second chamber oil passage;
A spool accommodated in the inner periphery of the valve body, the large diameter portion sliding on the inner periphery of the valve body between the first valve opening and the fixed portion, and the large diameter portion adjacent to the large diameter portion. provided at a position facing the large diameter portion and an intermediate shaft portion that forms an introduction passage that is connected to the axial passage through the first valve opening between itself and the inner circumference of the valve body. a middle diameter portion sliding on the inner peripheral surface of the valve body located on the rear end side from the second valve opening and having a smaller diameter than the large diameter portion and a larger diameter than the intermediate shaft portion; and a rear end shaft portion provided closer to the rear end portion than the intermediate shaft portion;
a spring provided between the fixing portion and the spool on the inner circumference of the valve body and biasing the spool toward the rear end portion;
A variable displacement oil pump characterized by comprising:
In the variable displacement oil pump according to claim 3,
The control valve has a solenoid portion at the rear end portion of the valve body for urging the rear end shaft portion of the spool from the rear end portion toward the tip portion in response to an electric signal applied from the outside. A variable displacement oil pump characterized by
In the variable displacement oil pump according to claim 3,
The spool has a spool drain hole that opens in the rear end shaft portion in the radial direction, and a drain connection passage that connects the spool drain hole and the inside of the spring,
The variable capacity valve body is characterized in that the valve body communicates with a space formed between the rear end shaft portion and the sleeve and has a third valve opening provided at a position facing the external connection path. shape oil pump.
In the variable displacement oil pump according to claim 1,
The control valve is
A valve body formed in a cylindrical shape, extending from a front end portion toward a rear end portion on the opposite side of the front end portion, and having a hole opening in the front end portion and a hole portion provided in the radial direction of the valve body. a valve body having a second chamber opening that communicates with the second chamber oil passage, and an external connection passage that communicates with an outside having a lower pressure than the pressure of the oil discharged from the discharge portion;
Inside the valve body, a sleeve fixed to the tip portion side and extending from the tip portion toward the rear end portion has a sleeve axial opening facing the hole, and the sleeve axial opening. a sleeve radial opening provided radially on the rearward end side of the sleeve;
a spool disposed between the inner periphery of the valve body and the outer periphery of the sleeve, the spool extending from the distal end toward the rearward end between the sleeve axial opening and the sleeve radial opening; a large-diameter portion that slides on the inner circumference of the valve body; an intermediate shaft portion that is provided adjacent to the large-diameter portion and forms an introduction passage with the inner circumference of the valve body; A spool radial opening that opens in the intermediate shaft portion and communicates with the sleeve radial opening; A medium-diameter portion that is formed to be larger than the shaft portion and smaller than the large-diameter portion and that slides on the inner circumference of the valve body, and a medium-diameter portion that is provided at a position adjacent to the medium-diameter portion and is located adjacent to the inner circumference of the valve body. a trailing shaft forming a discharge passage therebetween;
a spool biasing member that biases the spool toward the rear end;
A variable displacement oil pump characterized by comprising:
In the variable displacement oil pump according to claim 6,
The control valve has a solenoid portion at the rear end portion of the valve body for urging the rear end shaft portion of the spool from the rear end portion toward the tip portion in response to an electric signal applied from the outside. A variable displacement oil pump characterized by
In the variable displacement oil pump according to claim 1,
A variable displacement oil pump, wherein the volume of the second chamber increases when the adjusting member moves in a direction in which the flow rate of the oil discharged from the discharge portion increases.
In the variable displacement oil pump according to claim 8,
The pump structure is arranged such that the center of the inner periphery of the adjustment member and the rotation axis of the drive shaft of the pump structure are eccentric, and the adjustment member swings around a swing fulcrum. Capacitive oil pump.
In the variable displacement oil pump according to claim 9,
The control valve is provided such that the tip portion overlaps the adjustment member provided between the first chamber and the second chamber when viewed in a direction along the rotation axis. , wherein the rear end opposite to the front end is provided outside the second chamber.
In the variable displacement oil pump according to claim 9,
The variable displacement oil, wherein the connection path is arranged between the swing fulcrum of the adjustment member and the drive shaft of the pump assembly when viewed in the direction along the rotation axis. pump.
In the variable displacement oil pump according to claim 11,
the first chamber oil passage is open on the swing fulcrum side of the first chamber in the radial direction when viewed in the direction along the rotation axis;
A variable displacement oil pump, wherein the second chamber oil passage opens on the swing fulcrum side of the second chamber in the radial direction when viewed along the rotation axis.
In the variable displacement oil pump according to claim 11,
A variable displacement oil pump, wherein an inlet for introducing oil from the main gallery is provided between the first chamber and the connecting passage.
In the variable displacement oil pump according to claim 8,
The pump structure is arranged such that the center of the inner circumference of the adjustment member and the axis of rotation of the drive shaft of the pump structure are eccentric,
A variable displacement oil pump, wherein the adjustment member moves linearly.
In the variable displacement oil pump according to claim 1,
A variable displacement oil pump, wherein the volume of the second chamber increases when the adjusting member moves in a direction in which the flow rate of the oil discharged from the discharge portion decreases.
a housing having a pump chamber;
an adjustment member movably provided inside the pump housing chamber;
A pump structure provided in the adjustment member, which is driven to rotate and discharges oil sucked from a suction part from a discharge part, and when the adjustment member moves, the oil is discharged from the discharge part. the pump arrangement that varies the flow rate of
A flow rate of oil discharged from the discharge portion is formed between the pump housing chamber and the adjustment member in a radial direction with respect to the rotation axis of the pump structure, and the oil discharged from the discharge portion is guided. a first chamber whose volume increases when the adjustment member moves in a direction in which the
Oil provided at a position adjacent to the first chamber and the second chamber when viewed from the direction along the rotation axis of the pump structure, and to which oil that has passed through the main gallery from the first chamber side is guided. a linear oil passage portion formed at a position connecting the first chamber and the second chamber at the shortest distance when viewed from the direction along the rotation axis of the pump assembly; a first chamber oil passage branched from the oil passage portion and connected to the first chamber; a second chamber oil passage branched from the straight oil passage portion and connected to the second chamber; an oil passage having an external connection passage branched and connected to the outside having a lower pressure than the pressure of the oil discharged from the discharge portion;
a control valve provided on the linear oil passage portion, the control valve connecting the second chamber oil passage to a tip side passage provided at a tip portion of the control valve;
Variable displacement oil pump with