WO2020195077A1

WO2020195077A1 - Variable displacement pump

Info

Publication number: WO2020195077A1
Application number: PCT/JP2020/002448
Authority: WO
Inventors: 大輔加藤; 浩二佐賀
Original assignee: 日立オートモティブシステムズ株式会社
Priority date: 2019-03-22
Filing date: 2020-01-24
Publication date: 2020-10-01
Also published as: JP2020153330A

Abstract

A variable displacement pump of an internal combustion engine comprises: a housing having a pump accommodation part formed therein; a pump structure accommodated in the pump accommodation part and configured to be driven to rotate thereby to change the volume of a plurality of pump chambers to eject oil guided from a suction part to an ejection part; a bore provided to enable communication between ends in an axial direction and allow the oil ejected from the plurality of pump chambers to flow therethrough, the bore being a control ring movable according to the state of the internal combustion engine, the control ring forming a portion of the pump structure and having the plurality of pump chambers disposed therein; and a dividing member for dividing the bore into a plurality of bores, wherein the control ring moves to change the amount of oil being ejected from the ejection part.

Description

Variable displacement pump

The present invention relates to, for example, a variable displacement pump.

For example, as a variable displacement pump applied to an internal combustion engine for an automobile, a technique as described in Patent Document 1 is known.

In Patent Document 1, the oil discharged from the pump configuration of the variable displacement pump is discharged to the outside of the variable displacement pump through a hole provided in a control ring forming a part of the pump configuration. Was there.

Japanese Unexamined Patent Publication No. 2012-172516

However, in the technique described in Patent Document 1, the control ring is deformed by the pressure of the oil pressurized by the pump component during the operation of the variable displacement pump. Due to this deformation of the control ring, the sliding resistance of the movable part in the pump structure may increase, and the efficiency may deteriorate.

An object of the present invention is to provide a variable displacement pump capable of suppressing deterioration of efficiency.

According to one embodiment of the present invention, a housing having a pump accommodating portion formed therein and a suction portion in which the volumes of a plurality of pump chambers are changed by being accommodated in the pump accommodating portion and driven to rotate. A pump structure that discharges oil derived from the above to a discharge unit and a part of the pump structure are formed, and a plurality of pump chambers are arranged inside so that the pump can be moved according to the state of the internal combustion engine. A control ring that is provided so as to communicate with both ends in the axial direction and through which oil discharged from the plurality of pump chambers flows, and a dividing member that divides the holes into a plurality of holes. The control ring is provided with a control ring that changes the amount of oil discharged from the discharge unit by moving.

According to one embodiment of the present invention, it is possible to provide a variable displacement pump capable of suppressing deterioration of efficiency.

It is external perspective view which incorporated the variable capacity type pump into the internal combustion engine which concerns on embodiment of this invention. It is sectional drawing which cut in the axial direction of the crankshaft which concerns on embodiment of this invention. It is an exploded perspective view of the variable displacement type pump seen from the control housing side which concerns on embodiment of this invention. It is an exploded perspective view of the variable displacement type pump seen from the pump housing side which concerns on embodiment of this invention. It is a side view of the variable displacement type pump seen from the control housing side which concerns on 1st Embodiment of this invention. FIG. 5 is a sectional view taken along line VI-VI. It is a system block diagram of the variable capacity type pump which concerns on embodiment of this invention. FIG. 7 is a sectional view taken along line VIII-VIII in FIG. It is a side view which saw through the variable capacity type pump which concerns on embodiment of this invention. It is a side view of the variable capacity type pump which shows the state which attached the pump cover to the control housing which concerns on embodiment of this invention. It is an enlarged perspective view of the main part of the variable displacement type pump which concerns on embodiment of this invention. It is an enlarged view of the main part of the variable displacement type pump which concerns on embodiment of this invention. FIG. 12 is a sectional view taken along line XIII-XIII in FIG. It is a partially enlarged view of the pump housing which shows the state which removed the control ring from the variable displacement type pump which concerns on embodiment of this invention. FIG. 5 is a partially enlarged view showing a state in which the eccentricity of the control ring of the variable displacement pump according to the embodiment of the present invention is 100%. It is a partially enlarged view which shows the state which the eccentricity amount of the control ring of the variable displacement type pump which concerns on embodiment of this invention is 0%.

Hereinafter, embodiments of the variable displacement pump according to the present invention will be described in detail with reference to the drawings. In this embodiment, oil (lubricating oil) is supplied to the sliding portion of an internal combustion engine for automobiles, and a variable capacity that supplies hydraulic pressure as an operating source of a variable valve mechanism that changes the valve timing of the engine valve. The one applied to the type pump is shown.

The variable displacement pump in this embodiment is applied to the vane type and is provided at the front end of the cylinder block of the internal combustion engine.

FIG. 1 is an external perspective view in which a variable displacement pump is incorporated in an internal combustion engine according to an embodiment of the present invention, and FIG. 2 is a cross-sectional view cut along the axial direction of a crankshaft which is a rotating shaft according to the embodiment of the present invention. Is. In FIGS. 1 and 2, a variable displacement pump 120 is attached to the end of the cylinder block 111 of the internal combustion engine 110. Inside the cylinder block 111, there is provided a crankshaft 3 that converts the vertical movement of the piston arranged in the internal combustion engine 110 into a rotational movement via a connecting rod. The variable displacement pump 120 is provided with a rotor 4 described later. A penetrating opening 4b is formed in the central portion of the rotor 4, and the crankshaft 3 is inserted into the opening 4b and fixed. As a result, the rotational force of the crankshaft 3 is transmitted to the rotor 4.

Next, the configuration of the variable displacement pump will be described with reference to FIGS. 3 to 10. FIG. 3 is an exploded perspective view of the variable displacement pump as viewed from the control housing side according to the embodiment of the present invention, and FIG. 4 is an exploded perspective view of the variable displacement pump as viewed from the pump housing side according to the embodiment of the present invention. FIG. 5 is a side view of the variable displacement pump as viewed from the control housing side according to the embodiment of the present invention. 6 is a sectional view taken along line VI-VI in FIG. 5, FIG. 7 is a system configuration diagram of a variable displacement pump according to an embodiment of the present invention, and FIG. 8 is a sectional view taken along line VIII-VIII in FIG. FIG. 9 is a perspective view of the variable displacement pump according to the embodiment of the present invention, and FIG. 10 is a side view of the variable displacement pump showing a state in which the pump cover is attached to the control housing according to the embodiment of the present invention. is there.

As shown in FIGS. 3 to 6, the variable displacement pump is rotatably housed in a bottomed cylindrical pump housing 1 having an opening closed by a pump cover 2 and a pump housing 1 and a center thereof. The rotor 4 to which the crankshaft 3 is inserted and connected to the opening 4b of the above, the control ring 5 which is a movable member which is swingably arranged on the outer peripheral side of the rotor 4 and into which the crankshaft 3 is inserted, and the pump cover 2 The control housing 6 is provided on the outer surface of the control housing 6 and is mainly composed of a pilot valve 7 which is a control mechanism for controlling hydraulic pressure supply switching in order to swing the control ring 5. The crankshaft 3 penetrates substantially the center of the pump housing 1. Further, a solenoid valve 100, which is a switching mechanism described later, is connected to the variable displacement pump.

As shown in FIGS. 3 and 5, the pump housing 1, the pump cover 2, and the control housing 6 are integrally connected by a plurality of bolts 9, and each of the bolts 9 is integrally connected to the pump housing 1, the control housing 6, and the control housing 6. These are fastened by inserting them into the bolt insertion holes formed in the pump cover 2 respectively.

The pump housing 1 is integrally formed of a material containing aluminum such as an aluminum alloy, and the bottom surface of the concave pump accommodating portion 1s slides on one side surface in the axial direction of the control ring 5, so that the flatness, surface roughness, etc. The precision of the machine is high, and the sliding range is formed by machining. In this embodiment, the pump housing 1, the pump cover 2, and the control housing 6 form a housing that serves as a housing for the variable displacement pump, and a pump housing portion is formed inside the housing.

Further, as shown in FIGS. 3, 4, and 6, the pump housing 1 is formed with a bearing hole 1d for bearing one end of the crankshaft 3 penetrating at a substantially central position on the bottom surface of the pump accommodating portion 1s which is an operating chamber. At the same time, a bottomed pin hole 1c into which a pivot pin 10 (shaft member), which is a pivot pin serving as a pivot point of the control ring 5, is inserted is formed at a predetermined position on the inner peripheral surface. ..

Further, a first sealing surface 1a formed in an arc concave shape is formed on the inner peripheral side of the pump accommodating portion 1s at a position above the vertical direction. On the other hand, an arcuate concave second sealing surface 1b is formed on the inner peripheral side of the pump accommodating portion 1s at a position lower in the vertical direction.

The first sealing surface 1a seals the first control oil chamber 16 described later with the first sealing member 13 fitted in the first sealing groove 5b formed in the control ring 5 with a constant sliding contact. It has become. The first sealing mechanism is composed of the first sealing surface 1a and the first sealing member 13.

On the second sealing surface 1b, the second sealing member 14 described later, which is fitted in the second sealing groove 5c formed in the control ring 5, is constantly in sliding contact with the second sealing oil chamber 17 described later. ing. The second sealing mechanism is composed of the second sealing surface 1b and the second sealing member 14.

Further, as shown in FIG. 7, the first seal surface 1a and the second seal surface 1b are formed in an arcuate shape having a predetermined length centered on the pivot pin 10, and the control ring 5 swings eccentrically. Within the range, the first seal member 13 and the second seal member 14 are set to a length that allows constant sliding contact.

Further, as shown in FIGS. 3 and 4, the pump cover 2 is formed with a suction port 11 (suction portion) which is a suction portion having a substantially crescent-shaped notch shape, and the suction port 11 is provided with a radial suction portion. Discharge ports 12 (discharging portions), which are substantially crescent-shaped ejection portions, are formed at positions on opposite sides so as to be substantially opposed to each other. The specific configuration of the suction port 11 and the discharge port 12 will be described later.

As shown in FIGS. 3 and 4, the pump cover 2 is formed of an aluminum alloy material in a substantially plate shape, and a bearing hole 2a that rotatably supports the other end of the crankshaft 3 is formed through the pump cover 2 at a substantially central position. At the same time, a plurality of boss portions forming bolt insertion holes are integrally formed on the outer peripheral portion. Further, the pump cover 2 is coupled to the pump housing 1 by a plurality of bolts 9 while being positioned in the circumferential direction on the pump housing 1 via a plurality of positioning pins (not shown).

The rotational force transmitted from the crankshaft 3 is transmitted to the rotor 4, and the rotor 4 is rotated in the direction of the arrow (clockwise) in FIG. 7, and is the left half of the figure centered on the crankshaft 3. Is the suction area, and the right half is the discharge area.

In the rotor 4, as shown in FIGS. 3 and 4, nine vanes 15 are slidably held in the nine slits 4a formed radially outward from the inner center side so that the nine vanes 15 can move forward and backward (appearance possible). At the same time, a back pressure chamber 24 having a substantially circular cross section is formed at the base end of each slit 4a to introduce the discharge hydraulic pressure discharged to the discharge port 12. The vane 15 is pushed outward by the pressure in each back pressure chamber 24 and the centrifugal force accompanying the rotation of the rotor 4.

In each vane 15, each base end edge is in sliding contact with the outer peripheral surfaces of a pair of front and rear vane rings 18 and 18, and each tip edge is in sliding contact with the inner peripheral surface 5a of the control ring 5. .. Further, a plurality of pumps having a plurality of hydraulic oil chambers between the adjacent vanes 15 and the inner peripheral surface 5a of the control ring 5 and the inner peripheral surface of the rotor 4, the pump accommodating portion 1s, and the inner surface of the pump cover 2. The chambers 19 are liquidtightly separated. Each vane ring 18 pushes each vane 15 out of the radiation as it rotates, and even when the engine speed is low and the centrifugal force or the pressure of the back pressure chamber 24 is small, each vane 15 is Each tip of the pump chamber 19 is in sliding contact with the inner peripheral surface of the control ring 5, and each pump chamber 19 is liquid-tightly separated.

Therefore, when the rotational force transmitted from the crankshaft 3 is transmitted to the rotor 4, the volume of the pump chamber 19 increases from the state where the volume is the smallest, reaches the maximum volume, and then decreases. The region where the volume of the pump chamber 19 expands becomes the suction region, and the region where the volume decreases becomes the discharge region.

In the case of the present embodiment, the vane 15, the rotor 4, and the control ring 5 which are housed in the pump housing unit 1s and constitute the pump chamber 19 form the pump body.

The control ring 5, which constitutes a part of the pump structure, is integrally formed in a substantially cylindrical shape by a sintered metal of an iron-based material that is easy to process, and as shown in FIGS. 3, 4, and 7, the outer peripheral surface thereof. A pivot recess 5d is formed at the position of the pivot pin 10, and the pivot pin 10 inserted and positioned in the pivot recess 5d is inserted and inserted to serve as an eccentric swing fulcrum.

Further, at a position on the lower side of the pivot recess 5d of the control ring 5, holes 25 (

holes

25a and 25b) communicating with the discharge port 12 are formed through, and a second seal groove 5c is formed through the second seal groove 5c. A substantially triangular second protrusion 5g for holding the seal member 14 is provided. The hole 25 is provided on the side of the plurality of pump chambers 19 closest to the pump chamber 19 having the smallest volume in the section where the volume of the plurality of pump chambers 19 decreases with the rotational drive of the pump components. That is, the hole 25 is between the intermediate position of the section where the volume of the pump chamber decreases in the circumferential direction with the rotational drive of the pump configuration and the terminal portion of the discharge port 12 closest to the pump chamber having the smallest volume. It is provided in.

Further, at a position on the upper side of the control ring 5, a substantially triangular first protrusion 5h for holding the first seal member 13 is provided via the first seal groove 5b. The hole 25 is rectangular and is provided along the rotation axis of the rotor 4 which is a part of the pump structure, and the oil discharged from the pump structure flows through the hole 25 in communication with the discharge port 12. The hole portion 25 is divided into a plurality of

holes

25a and 25b by a dividing member 37 (partitioning member). The dividing member 37 divides the hole 25 into two

holes

25a and 25b in the radial direction with respect to the rotation axis of the rotor 4, which is a part of the pump structure. The configuration of the hole 25 will be described later. The dividing member 37 may divide the hole 25 into a plurality of two or more holes.

As shown by the arrow in FIG. 8, the oil is discharged from the discharge port 12, and a part of the oil on the attachment side to the cylinder block 111 (lower side in FIG. 8) passes through the plurality of

holes

25a and 25b. It is guided to the discharge passage 61.

The pump component is housed inside the pump accommodating portion and is driven to rotate to discharge the oil guided from the suction port 11 (inhalation portion) from the discharge port 12 (discharge portion). Further, the rotor 4, the vane 15, the vane ring 18, and the control ring 5 are made of an iron-based material.

A first control oil chamber 16 is formed on the upper side centering on the control ring 5 between the outer peripheral surface of the control ring 5 on the first protrusion 5h and the second protrusion 5g side and the pump housing 1. A second control oil chamber 17 is formed on the lower side, respectively.

The first control oil chamber 16 reduces the control ring 5 by the hydraulic pressure supplied to the inside, which is one of the directions in which the eccentricity changes against the spring force of the coil spring 28 described later (from the pump configuration). It is designed to press in the direction in which the amount of discharged oil decreases). That is, the first control oil chamber 16 is a reduction side control chamber.

The oil discharged from the discharge port portion is guided to the first control oil chamber 16 through the discharge hole 12a, the main oil gallery 31, the second oil gallery 33, and the first control groove 35, and the oil discharge amount is increased. It is configured to increase the volume of the pump chamber as the control ring moves in a decreasing direction. Further, the first control oil chamber 16 is configured to communicate with or be cut off from the discharge port 12 via the pilot valve 7, and is always provided by the first seal mechanism even when the control ring 5 swings. It is designed to be liquidtightly sealed.

The second control oil chamber 17 assists the control ring 5 with the spring force of the coil spring 28 described later by the hydraulic pressure supplied to the inside to urge the control ring 5 in a direction in which the amount of eccentricity increases, and the solenoid valve 100 Hydraulic pressure is supplied or discharged via the solenoid valve 7. That is, the second control oil chamber 17 is an increasing side control chamber.

Further, since the distance from the eccentric swing fulcrum to the second seal member 14 is set to be larger than the distance to the first seal member 13, the outer surface of the control ring 5 on the second control oil chamber 17 side. The area of the second pressure receiving surface 20 is larger than the area of the first pressure receiving surface 21 which is the outer surface on the side of the first control oil chamber 16.

Therefore, the pressing force on the control ring 5 by the hydraulic pressure in the second control oil chamber 17 is slightly offset by the opposite hydraulic pressure in the first control oil chamber 16, and as a result, the control ring 5 is pivoted by the discharge oil pressure. The force that attempts to reduce the amount of eccentricity by swinging counterclockwise with the pin 10 as a fulcrum becomes smaller, and the spring force of the coil spring 28 described later that urges the control ring 5 clockwise in opposition to this becomes smaller. Can be set small.

The first seal member 13 and the second seal member 14 are formed of, for example, a low-wear synthetic resin material elongated along the axial direction of the control ring 5, and the first protrusions 5h and the second of the control ring 5 are formed. It is held in the first seal groove 5b and the second seal groove 5c formed on the outer peripheral surface of the protrusion 5g. Further, the first seal member 13 and the second seal member 14 are moved forward by the elastic force of the rubber elastic members 13a and 14a fixed to the bottom side of the first seal groove 5b and the second seal groove 5c, that is, each seal. It is designed to be pressed against the

surfaces

1a and 1b. As a result, good liquidtightness of the first control oil chamber 16 and the second control oil chamber 17 is always ensured.

As shown in FIGS. 7 and 9, the suction port 11 is open to a region where the volume of each pump chamber 19 is expanded, and is substantially centered by the negative pressure generated by the pumping action of the pump structure. The oil in the oil pan 55 is introduced through the formed suction port 11a.

A spring accommodating chamber 27 for accommodating the coil spring 28 is formed in the pump housing 1 and communicates with the suction port 11a. The suction port 11a communicates with the low pressure chamber 22 together with the spring accommodating chamber 27, and sucks oil sucked from the oil pan 55 through the suction passage by the negative pressure generated by the pumping action of the pump component. It is supplied to 11 and is supplied to each pump chamber 19 whose volume has been expanded. Therefore, the entire suction port 11, suction port 11a, spring accommodating chamber 27, and low pressure chamber 22 are configured as a low pressure portion.

On the other hand, the discharge port 12 is open to a region where the volume of each pump chamber 19 is reduced due to the pumping action of the pump structure, and the discharge hole 12a formed in the pump housing 1 is used through the main oil gallery 31. It communicates with each sliding part of the engine and, for example, a valve timing control device which is a variable valve gear. A filter 34 for removing impurities of oil is installed in the middle of the main oil gallery 31.

As shown in FIG. 7, the control ring 5 is integrally provided with an arm 26 which is an extending portion protruding outward in the radial direction at a position opposite to the pivot recess 5d on the outer peripheral surface of the tubular body. The arm 26 is urged by a coil spring 28 to swing the control ring 5.

Further, a spring accommodating chamber 27 is formed at a position below the arm 26 of the pump housing 1.

The spring accommodating chamber 27 is formed in a substantially flat rectangular shape extending along the axial direction of the pump housing 1, and internally, the control ring 5 is urged clockwise in FIG. 7 via the arm 26, that is, The control ring in the direction of increasing eccentricity between the center of rotation of the rotor 4 and the center of the inner peripheral surface of the control ring 5 (the direction in which the amount of oil discharged from the pump component increases). A coil spring 28, which is an urging member for urging 5, is housed and arranged. The spring accommodating chamber 27 communicates with the low pressure chamber 22 via the suction port 11.

The lower end edge of the coil spring 28 (biasing member) is in contact with the bottom surface of the spring accommodating chamber 27, while the upper end edge is in elastic contact with the arm 26, and a predetermined spring load W is applied in the spring accommodating chamber 27. The upper end edge is constantly in contact with the arm 26 and is urged in a direction in which the amount of eccentricity between the center of rotation of the rotor 4 in the control ring 5 and the center of the inner peripheral surface of the control ring 5 increases.

That is, the coil spring 28 is urged in a direction in which the control ring 5 is always eccentric upward via the arm 26 in a state where the spring load W is applied, that is, in a direction in which the volume of each pump chamber 19 increases. The spring load W is a load that is introduced only into the first control oil chamber 16 and the control ring 5 starts to move when the hydraulic pressure is the required hydraulic pressure P1 of the valve timing control device.

Further, a regulating portion 29 is formed at a position facing the spring accommodating chamber 27 of the pump housing 1 in the axial direction so that the upper surface of the arm 26 abuts and regulates the maximum clockwise rotation position of the arm 26.

Then, as shown in FIG. 7, the pump housing 1 is formed with a discharge pressure introduction hole 30, and the first control groove 35 and the first control groove 35 communicating with the first control oil chamber 16 and the second control oil chamber 17 are formed. Two control grooves 36 are formed respectively.

The discharge pressure introduction hole 30 communicates with the hydraulic pressure introduction port 45 described later of the pilot valve 7.

The first control groove 35 is connected to the second oil gallery 33 via a control groove 35b (FIGS. 9 and 10) whose one end is also opened in the pump cover 2.

On the other hand, the second control groove 36 branches from the first control groove 35 and communicates with the second control oil chamber 17.

The oil discharged from the discharge port 12 formed in the pump cover 2 is guided to the discharge passage 61 from the discharge opening 60 formed in the control housing 6 and flows toward the discharge hole 12a. The discharge port 12 and the discharge passage 61 are connected to each other. The configuration of the discharge passage 61 will be described later.

As shown in FIGS. 3, 4, and 7, the pilot valve 7 is integrally provided on one side of the outer surface of the control housing 6 in the vertical direction, and has a cylindrical valve body 40 whose upper portion is closed and a valve body. A spool valve 42 that is slidable in the vertical direction in the valve accommodating portion 41 formed inside the 40, a plug 43 that closes the lower end opening of the valve accommodating portion 41, and a bullet between the spool valve 42 and the plug 43. It is equipped with a valve spring 44, which is mounted and urges the spool valve 42 upward. The spool valve 42 controls the supply and discharge of hydraulic pressure to the second control oil chamber 17 by means of a pair of large diameter portions, a first land portion 42a and a second land portion 42b.

The valve body 40 is formed with an introduction port 46, which is an introduction passage opening connected to the solenoid valve 100. Further, on the peripheral wall of the valve accommodating portion 41, one end side is connected to the second control oil chamber 17 and the other end side is always connected to the relay chamber 47, which will be described later, at an intermediate position in the axial direction, so that the second control oil is connected. A hydraulic pressure introduction port 45, which is an opening of a control oil chamber for supplying and discharging hydraulic pressure to the chamber 17, is formed, and one end side is directly connected to the outside or the suction side at a position on the other end side in the axial direction. By switching the connection with the relay chamber 47, which will be described later, the first drain port 48, which is a control drain opening for discharging the hydraulic pressure in the second control oil chamber 17, is formed through the relay chamber 47. Similar to the first drain port 48, the valve body 40 is directly connected to the outside or the suction side at the axial position of the peripheral wall on one end side and overlapping the back pressure chamber 52 described later in the radial direction. 2 Drain port 49 is formed as an opening. The first drain port 48 and the second drain port 49 communicate with the oil pan 55, and the oil discharged from the first drain port 48 and the second drain port 49 is stored in the oil pan 55.

Further, on the peripheral wall portion of the valve body 40, a communication oil passage 50 for communicating the introduction port 46 and the relay chamber 47, which will be described later, is configured with the spool valve 42 at the position on the upper end side in FIG. ing.

The spool valve 42 is provided with a first land portion 42a and a second land portion 42b at both ends in the axial direction, and a shaft portion 42c having a small diameter between the first land portion 42a and the second land portion 42b. Is provided. Then, by accommodating the spool valve 42 in the valve accommodating portion 41, the spool valve 42 is provided in the valve body 40 on the axially outer side of the first land portion 42a and is introduced between the spool valve 42 and one end portion of the valve body 40. The pressure chamber 51 from which the discharge pressure is guided from the port 46 is provided between the first land portion 42a and the second land portion 42b, and the hydraulic pressure introduction port 45 and the introduction port 46 (communication oil passage) are provided depending on the axial position of the spool valve 42. 50) or the relay chamber 47 that relays the first drain port 48 and the plug 43 on the axially outer side of the second land portion 42b, and relays through the outer peripheral side (micro gap) of the second land portion 42b. The back pressure chamber 52 used to discharge the oil leaked from the chamber 47 is separated from each other.

With such a configuration, in the pilot valve 7, when the discharge pressure guided from the introduction port 46 to the pressure chamber 51 is equal to or less than a predetermined pressure, the spool valve 42 is on the upper end side of the valve accommodating portion 41 with the urging force of the valve spring 44. It will be located in the first region, which is a predetermined region of (see FIG. 7). That is, since the spool valve 42 is located in the first region, the introduction port 46 and the relay chamber 47 are connected to each other via the communication oil passage 50, while the first drain port 48 and the relay chamber 47 are connected by the second land portion 42b. As a result of the connection of the second control oil chamber 17 and the relay chamber 47 being connected via the hydraulic pressure introduction port 45, the hydraulic pressure guided from the introduction port 46 through the communication oil passage 50 is passed through the relay chamber 47. 2 It will be supplied to the control oil chamber 17.

Then, when the discharge pressure guided to the pressure chamber 51 exceeds a predetermined pressure, the spool valve 42 moves from the first region to the lower end side of the valve accommodating portion 41 against the urging force of the valve spring 44, and the valve It will be located in the second region, which is a predetermined region on the lower end side of the accommodating portion 41 (not shown). That is, by locating the spool valve 42 in the second region, the second control oil chamber 17 is maintained in connection with the relay chamber 47 via the hydraulic introduction port 45, while the communication oil passage is maintained by the first land portion 42a. The connection between the 50 and the relay chamber 47 is cut off, and as a result of connecting the relay chamber 47 and the oil pan 55 via the first drain port 48, the oil in the second control oil chamber 17 flows through the relay chamber 47 to the first drain. It will be discharged to the oil pan 55 through the port 48.

Further, the pilot valve 7 is operated by the solenoid 56, and the solenoid 56 is energized with an exciting current from an in-vehicle ECU (not shown) via the connector portion 57.

As shown in FIG. 7, the solenoid valve 100 is interposed in the middle of the first oil gallery 32, and the substantially cylindrical valve body 101 having an oil passage 102 penetrating along the internal axial direction and the valve body 101 thereof. At one end of the valve body 101 (the left end in the figure), the oil passage 102 is expanded and fixed to the outer end of the valve body accommodating portion 103, and the first oil gallery 32 is located at the center thereof. It is formed on a seat member 105 having an introduction port 104 which is an upstream opening connected to an upstream passage (hereinafter, simply referred to as "upstream passage") 32a, and an inner end opening edge of the seat member 105. A ball valve body 106 that can be detached and seated from the valve seat 105a to open and close the introduction port 104, and a solenoid 107 provided at the other end of the valve body 101 (the right end in the figure). , Is mainly composed of.

The valve body 101 is provided with a valve body accommodating portion 103 accommodating the ball valve body 106 on the inner peripheral portion on one end side in a stepped diameter expansion with respect to the oil passage 102. A supply / discharge port, which is a downstream opening that is connected to the downstream passage 32b and is used for supplying and discharging hydraulic pressure to the pilot valve 7 on the outer peripheral portion of the valve body accommodating portion 103, which is one end side of the peripheral wall of the valve body 101. The 108 is formed to penetrate along the radial direction, and the drain port 109, which is a switching drain opening connected to the oil pan 55, penetrates along the radial direction on the outer peripheral portion of the oil passage 102 on the other end side. It is formed.

The solenoid 107 has an armature (not shown) arranged on the inner peripheral side of the coil and a rod fixed thereto by an electromagnetic force generated by energizing a coil (not shown) housed inside the casing 107a. The 107b is configured to advance and move to the left in FIG. The solenoid 107 is energized with an exciting current from an in-vehicle ECU (not shown) based on the engine operating state detected or calculated by predetermined parameters such as the oil temperature and water temperature of the internal combustion engine and the engine speed. It becomes.

From such a configuration, when the solenoid 107 is energized, the rod 107b is advanced and moved, so that the ball valve body 106 arranged at the tip of the rod 107b is pressed against the valve seat 105a on the seat member 105 side and introduced. The communication between the port 104 and the supply / discharge port 108 is cut off, and the supply / discharge port 108 and the drain port 109 communicate with each other through the oil passage 102. On the other hand, when the solenoid 107 is not energized, the ball valve body 106 moves backward based on the discharge pressure guided from the introduction port 104, so that the ball valve body 106 is pressed toward the valve body 101 and becomes the introduction port 104. The hydraulic pressure introduction port 45 is in a communication state, and the communication between the hydraulic pressure introduction port 45 and the drain port 109 is cut off.

By the way, as described above, in this embodiment, the oil discharged from the discharge port 12 formed in the pump cover 2 is guided to the discharge passage 61 from the discharge opening 60 formed in the control housing 6 and into the discharge hole 12a. It flows toward. The discharge hole 12a is located at a position away from the control ring support portion 65 and is formed in the discharge passage 61. The configuration of the discharge passage 61 will be described with reference to FIGS. 9 and 10.

As shown in FIGS. 9 and 10, the discharge passage 61 is provided with a control ring support portion 65 that supports the pivot pin 10 of the control ring 5. The control ring support portion 65 is formed to be gradually thinner toward the direction away from the rotation axis of the rotor 4 which is a part of the pump structure when viewed from the direction of the rotation axis of the rotor 4 which is a part of the pump structure. Has been done. In other words, the control ring support 65 is formed in a teardrop shape.

The oil discharged from the discharge opening 60 to the discharge passage 61 is divided into two flow paths by the control ring support portion 65, merges in the discharge passage 61, and then guided to the discharge hole 12a. The discharge passage 61 includes a first discharge passage 61a formed between the peripheral wall of the control ring support portion 65 and the peripheral wall of the discharge passage 61 in the rotation direction of the rotor 4, which is a part of the pump configuration, and the pump configuration. A second discharge passage 61b formed between the peripheral wall of the control ring support portion 65 and the peripheral wall of the discharge passage 61 in a direction opposite to the rotation direction of the rotor 4, which is a part of the rotor 4, is provided. The peripheral wall of the control ring support portion 65 forming the first discharge passage 61a and the peripheral wall of the discharge passage 61 are formed substantially parallel to each other along the oil flow direction. As a result, the oil can flow smoothly to the downstream side.

As described above, the control ring support portion 65 of the present embodiment is separated from the rotation shaft of the rotor 4 which is a part of the pump structure when viewed from the direction of the rotation shaft of the rotor 4 which is a part of the pump structure. It is characterized by having a so-called teardrop shape, which is gradually formed thinner in the direction.

Generally, when a flow collides with an object, the pressure increases at the collision site. On the other hand, on the downstream side of the collision site, the pressure drops sharply and peeling occurs (a vortex is generated). At the part where the peeling occurs, the flow is turbulent, and the turbulence causes a pressure loss, which reduces the efficiency of the pump. For example, when the control ring support portion 65 is formed in a columnar shape, the oil collides with the control ring support portion 65 at the upstream end 65a and peels off at the downstream end 65b where the first discharge passage 61a and the second discharge passage 61b merge. Will occur, resulting in pressure loss. In order to suppress the separation of the flow, it is effective to move the separation position to the downstream side and reduce the portion where the pressure drops sharply. Therefore, in this embodiment, the downstream end 65b of the control ring support portion 65 is set to a position extended to the downstream side. That is, the distance connecting the center of the pivot pin 10 and the downstream end 65b is longer than the distance connecting the center of the pivot pin 10 and the upstream end 65a. Then, the oil that collides with the control ring support portion 65 at the upstream end 65a is divided into the first discharge passage 61a and the second discharge passage 61b, and merges at the position where the oil has passed the downstream end 65b. In this embodiment, the control ring support portion 65 has a teardrop shape so that the oil flowing through the peripheral wall of the control ring support portion 65 can smoothly flow to the downstream side.

According to this embodiment, the control ring support portion 65 has a so-called teardrop shape in which the control ring support portion 65 is gradually formed to become thinner in the direction away from the rotation axis of the pump mechanism when viewed from the direction of the rotation axis of the pump mechanism. , The oil flow can be smoothed and the pressure loss of the pump can be reduced.

In the variable displacement pump of this embodiment, the second control oil chamber 17 and the first control oil chamber 16 are formed, and the second pressure receiving surface 20 which is the outer surface of the control ring 5 on the second control oil chamber 17 side. , And the first pressure receiving surface 21, which is the outer surface on the first control oil chamber 16 side, receives high pressure. Since the pressure acts toward the inner peripheral side of the control ring 5, the control ring 5 is deformed in the crushing direction. The control ring 5 is formed with a penetrating hole that communicates with the discharge port 12, and the hole reduces the rigidity of the control ring 5. Therefore, the control ring 5 is easily deformed by the pressure. When the control ring 5 is deformed, the inside of the control ring 5 changes from a perfect circular state to an elliptical state, and the rotation of movable parts in the pump configuration arranged inside the control ring 5 is hindered, which may increase the load. There is. A configuration for solving this problem will be described with reference to FIGS. 7 to 9 and 11 to 16.

FIG. 11 is an enlarged perspective view of a main part of the variable displacement pump according to the embodiment of the present invention, FIG. 12 is an enlarged view of the main part of the variable displacement pump according to the embodiment of the present invention, and FIG. 13 is FIG. XIII-XIII line sectional view, FIG. 14 is a partially enlarged view showing a state in which the control ring is removed from the variable displacement pump according to the embodiment of the present invention, and FIG. 15 is a partially enlarged view showing a state in which the control ring is removed from the variable displacement pump according to the embodiment of the present invention. FIG. 16 is a partially enlarged view showing a state in which the eccentricity of the control ring is maximum, and FIG. 16 is a partially enlarged view showing a state in which the eccentricity of the control ring of the variable displacement pump according to the embodiment of the present invention is the minimum.

As shown in FIGS. 11 and 12, the hole portion 25 of this embodiment is divided into a plurality of parts by the dividing member 37. In other words, the dividing member 37 is arranged between the

holes

25a and 25b. The dividing member 37 secures the rigidity of the control ring 5 and plays a role as a support as a reinforcing member for suppressing the deformation of the hole 25 when a pressure is applied to the control ring 5.

It is effective to form the dividing member 37 so as to extend in the radial direction from the inner circumference of the control ring 5 on which the discharge pressure acts to the outer circumference. However, depending on the shape of the control ring 5 and the location of the discharge region, the control ring 37 may be controlled. The ring 5 may be provided at an angle with respect to the radial direction.

In this embodiment, as shown in FIG. 7, the control ring 5 abuts on the coil spring 28 (biasing member) in the hole 25 in the radial direction with respect to the rotation axis of the rotor 4, which is a part of the pump structure. It is provided on the side (lower side in FIG. 7) where the coil spring 28 (biasing member) is arranged with respect to the reference line BL of the control ring 5 connecting the portion and the pivot pin 10 (shaft member). In other words, the hole 25 is provided on the side where the pressure of the oil to be pressurized and discharged becomes high. With this configuration, the pressure of the discharged oil can be increased.

Further, contrary to the above, the hole 25 is on the side where the coil spring 28 (biasing member) is arranged with respect to the reference line BL of the control ring 5 in the radial direction with respect to the rotation axis of the pump component. It may be provided on the opposite side (upper side in FIG. 7). That is, the hole 25 is provided on the side closer to the pump chamber 19 having the largest volume among the plurality of pump chambers 19 in the section where the volume of the plurality of pump chambers 19 decreases with the rotational drive of the pump components. May be. In the case of such an embodiment, the hole 25 is formed at an intermediate position of a section in which the volume of the pump chamber decreases in the circumferential direction as the pump component is rotationally driven, and a discharge port 12 closest to the pump chamber having the largest volume. It will be provided between the start and end of. In this case, the effect of being able to quickly discharge the pressurized oil can be expected.

In this embodiment, the dividing member 37 is integrally formed with the control ring 5. With this configuration, the

holes

25a and 25b can be easily formed in the control ring 5. Apart from this, the dividing member 37 may be formed separately from the control ring 5. For example, when the dividing member 37 is formed separately from the control ring 5, the dividing member 37 is made of a material harder than the control ring 5. In this case, since the dividing member 37 can be formed thin while ensuring the rigidity of the dividing member 37, the flow rate of the oil passing through the

holes

25a and 25b can be secured.

The dividing member 37 is provided at the center of the hole 25 in the circumferential direction in the radial direction with respect to the rotation axis of the pump component. With this configuration, the sizes of the

holes

25a and 25b can be configured to be substantially uniform, and the flow rate of oil passing through the

holes

25a and 25b can be ensured in a well-balanced manner.

As shown in FIG. 11, the control ring 5 is recessed in the direction along the rotation axis of the rotor 4, which is a part of the pump structure, and straddles the hole 25 and the dividing member 37 in the radial direction with respect to the rotation axis. It is provided with a groove portion 5e provided in the above. In this embodiment, oil can easily flow from the other pump chamber 19 adjacent to the one pump chamber 19 toward the one pump chamber 19 through the groove portion 5e, and the flow path resistance can be reduced.

Further, the groove portion 5e is formed to have a larger radial size (width) with respect to the rotation axis as it approaches the hole portion 25. In other words, the groove portion 5e is formed to have a larger radial size (width) with respect to the rotation axis on the downstream side (position where the hole portion 25 is located) than on the upstream side (upper side of FIG. 11).

Further, the groove portion 5e is formed so as to extend to the intermediate positions 5e1 and 5e2 on the outer side in the radial direction so as to overlap a part of the hole portion 25 in the circumferential direction of the rotation axis. Similarly, the groove portion 5e is formed so as to extend to the low position portion 37a which is an intermediate position on the radial outer side of the rotation axis in the dividing member 37. A high position portion 37b having a height higher than that of the low position portion 37a is formed on the outer side in the radial direction of the low position portion 37a in the direction along the rotation axis direction. In other words, the dividing member 37 is formed with stepped portions having different heights in the direction along the rotation axis.

As described above, the groove portion 5e of this embodiment is provided halfway between the hole portion 25 and the dividing member 37 in the radial direction with respect to the rotation axis.

Further, the groove portion 5e of this embodiment is formed to have a larger diameter in the radial direction with respect to the rotation axis as it approaches the hole portion 25.

Although the groove 5e has been described in FIGS. 11 and 12 on the side opposite to the mounting side of the cylinder block 111, the groove 5e of this embodiment is similarly formed on the mounting side of the cylinder block 111. There is. Then, as shown in FIG. 13,

oil passages

70 and 71 are formed in the control ring 5 by the groove portion 5e on the side opposite to the mounting side of the cylinder block 111 and on the mounting side of the cylinder block 111, respectively. Further, as shown in FIGS. 13 and 14, the pump housing 1 has an oil passage between the pump accommodating portion 1s and the control ring 5 in which the pump component is accommodating in the direction of the rotation axis. A recess 1e is formed.

Next, the relationship between the recess 1e and the control ring 5 will be described with reference to FIGS. 14 to 16.

The recess 1e has a shape recessed toward the cylinder block 111 in the direction of the rotation axis. In a state where the control ring 5 is arranged in the pump accommodating portion 1s, the control ring 5 and the recess 1e overlap each other when viewed from the direction of the rotation axis.

FIG. 15 shows a state in which the amount of eccentricity of the control ring 5 is maximum (100%). At this time, the holes 25 (

holes

25a and 25b) formed by the control ring 5 are entirely overlapped with the recess 1e. Since the entire holes 25 (

holes

25a and 25b) overlap with the recesses 1e, the oil discharged from the holes 25 (

holes

25a and 25b) flows smoothly without being hindered.

On the other hand, FIG. 16 shows a state in which the amount of eccentricity of the control ring 5 is the minimum (0%). At this time, the hole 25 (

holes

25a, 25b) formed by the control ring 5 overlaps a part of the recess 1e. Further, the groove portion 5e of the control ring 5 overlaps with the edge of the recess 1e of the pump housing 1 as surrounded by the dotted line in FIG. As a result, the amount of oil discharged from the holes 25 (

holes

25a and 25b) is adjusted to be narrowed down.

As described above, according to the present embodiment, the deformation of the control ring due to the internal pressure of the pump chamber 19 is suppressed, and between the control ring in the pump configuration and the movable portion that is moved by being rotationally driven. The increase in friction can be suppressed, and the deterioration of the efficiency of the variable displacement pump can be suppressed.

The present invention is not limited to the above-described embodiment, and includes various modifications. The above-described examples have been described in detail in order to explain the present invention in an easy-to-understand manner, and are not necessarily limited to those having all the described configurations.

Further, the present invention has mainly described an embodiment in which the control ring 5 swings with respect to the pivot pin 10, but when the control ring 5 slides straight, the center of the inner peripheral surface of the control ring 5 and the rotor 4 It can also be applied to variable displacement pumps whose eccentricity with the center of rotation changes.

Further, the present invention has mainly described an embodiment in which the pump component is a vane pump having a rotor 4, a vane 15, a vane ring 18, and a control ring 5, but the inscribed gear pump accommodating the inner rotor and the outer rotor Can also be applied. At this time, the control ring 5 is arranged on the outer circumference of the outer rotor, and the rotation center of the outer rotor is revolved around the rotation center of the inner rotor to change the amount of oil discharged from the pump configuration. it can.

That is, the present invention is not limited to the above-described embodiment, and includes various modifications. For example, the above-described embodiment has been described in detail in order to explain the present invention in an easy-to-understand manner, and is not necessarily limited to the one including all the described configurations. Further, it is possible to replace a part of the configuration of one embodiment with the configuration of another embodiment, and it is also possible to add the configuration of another embodiment to the configuration of one embodiment. Further, it is possible to add / delete / replace a part of the configuration of each embodiment with another configuration.

This application claims priority based on Japanese Patent Application No. 2019-054006 filed on March 22, 2019. The entire disclosure, including the specification, claims, drawings, and abstract of Japanese Patent Application No. 2019-054006 filed March 22, 2019, is incorporated herein by reference in its entirety.

1 ... Pump housing, 1c ... Pin hole, 1e ... Recess, 1s ... Pump housing, 2 ... Pump cover, 3 ... Crankshaft, 4 ... Rotor, 4b ... Opening, 5 ... Control ring, 5e ... Groove, 6 ... Control housing, 7 ... Pilot valve, 10 ... Pivot pin, 11 ... Suction port, 12 ... Discharge port, 12a ... Discharge hole, 13 ... First seal member, 14 ... Second seal member, 15 ... Vane, 16 ... First Control oil chamber, 17 ... 2nd control oil chamber, 18 ... vane ring, 19 ... pump chamber, 25 ... hole, 25a, 25b ... hole, 30 ... discharge pressure introduction hole, 31 ... main oil gallery, 32 ... 1st Oil gallery, 32a ... upstream passage, 32b ... downstream passage, 33 ... second oil gallery, 35 ... first control groove, 36 ... second control groove, 37 ... split member, 60 ... discharge opening, 61 ... discharge passage , 61a ... 1st discharge passage, 61b ... 2nd discharge passage, 65 ... control ring support, 65a ... upstream end, 65b ... downstream end, 70, 71 ... oil passage, 110 ... internal combustion engine, 111 ... cylinder block, 120 … Variable displacement pump

Claims

A variable displacement pump for internal combustion engines
A housing with a pump housing inside,
A pump configuration in which the volumes of the plurality of pump chambers are changed by being accommodated in the pump accommodating portion and driven to rotate, and the oil guided from the suction portion is discharged to the discharge portion.
A control ring that constitutes a part of the pump structure and has a plurality of pump chambers arranged therein so as to be movable according to the state of the internal combustion engine so as to communicate with both ends in the axial direction. It has a hole portion through which oil discharged from the plurality of pump chambers flows, and a dividing member for dividing the hole portion into a plurality of holes, and is discharged from the discharge portion by moving. The control ring that changes the amount of oil and
Variable displacement pump equipped with.
The variable displacement pump according to claim 1.
The hole is provided on the side closer to the pump chamber having the smallest volume among the plurality of pump chambers in a section in which the volume of the plurality of pump chambers decreases with the rotational drive of the pump component. Variable displacement pump.
The variable displacement pump according to claim 1.
The split member is a variable displacement pump integrally formed with the control ring.
The variable displacement pump according to claim 1.
The dividing member is a variable displacement pump provided at the center of the hole in the radial direction of the control ring.
The variable displacement pump according to claim 2.
The control ring is a variable displacement pump having a recess in the axial direction and a groove provided so as to straddle the hole and the dividing member in the radial direction.
The variable displacement pump according to claim 5.
A variable displacement pump in which the groove portion is formed so that the radial size of the control ring increases as it approaches the hole portion.
The variable displacement pump according to claim 5.
The groove portion is a variable displacement pump provided halfway between the hole portion and the dividing member in the radial direction of the control ring.
The variable displacement pump according to claim 7.
A variable displacement pump in which a step portion having different heights in the axial direction of the control ring is formed on the divided member.
The variable displacement pump according to claim 5.
The housing has a recess between the pump accommodating portion and the control ring.
The hole overlaps with the entire recess when the oil discharge rate is maximum.
The groove is a variable displacement pump that overlaps the edge of the recess when the amount of oil discharged is the minimum.
The variable displacement pump according to claim 1.
The hole is a rectangular variable displacement pump.
The variable displacement pump according to claim 1.
The pump structure and the control ring are variable displacement pumps made of an iron-based material.
The variable displacement pump according to claim 11.
The control ring is a variable displacement pump made of sintered metal.
The variable displacement pump according to claim 1.
The housing is a variable displacement pump made of a material containing aluminum.
The variable displacement pump according to claim 1.
The pump component is a variable displacement pump into which a crankshaft provided in the internal combustion engine is inserted and rotationally driven by the crankshaft.