WO2016021328A1

WO2016021328A1 - Hydraulic control valve and valve-timing control device for internal-combustion engine using hydraulic control valve

Info

Publication number: WO2016021328A1
Application number: PCT/JP2015/068489
Authority: WO
Inventors: 保英 ▲高▼田
Original assignee: 日立オートモティブシステムズ株式会社
Priority date: 2014-08-04
Filing date: 2015-06-26
Publication date: 2016-02-11
Also published as: JPWO2016021328A1

Abstract

Provided is a hydraulic control valve wherein the degree of freedom with which ports are laid out in the axial direction is improved and wherein structural components need not have high dimensional precision. A solenoid selector valve (21) that is provided with: a valve body (50) that is a cam bolt that connects a vane rotor (9) to one end part (2a) of a cam shaft (2); a cylindrical metal spool valve (51) that is provided inside the valve body so as to be slidable in the axial direction and that switches the state of the supply/discharge of a working fluid to and from a retard hydraulic chamber (11) and an advance hydraulic chamber (12); a sleeve (52) that comprises a synthetic resin material and that is inserted into and affixed inside the spool valve; and a solenoid (55) that moves the spool valve in the axial direction. The sleeve has a partitioning wall (52c) that has a cross-shaped cross-section and that radially partitions the inside of a retaining hole (59) that is inside the spool valve into four passageways (65a-65d) that are formed for the purpose of supply to and discharge from the hydraulic chambers.

Description

Hydraulic control valve and valve timing control device for an internal combustion engine using the hydraulic control valve

The present invention relates to, for example, a hydraulic control valve used in a valve timing control device that variably controls the valve timing of an intake valve or an exhaust valve of an internal combustion engine according to an operating state.

Various hydraulic control valves conventionally used in valve timing control devices for internal combustion engines have been provided, and one of them is described in Patent Document 1 below.

Briefly, this hydraulic control valve is a cylindrical valve body that is inserted and disposed inside a vane rotor that is fixed from one axial end of the camshaft in the axial direction, and is accommodated and fixed inside the valve body. A cylindrical sleeve, a spool valve slidably provided along the axial direction inside the sleeve, and a valve spring that biases the spool valve in one direction in the other direction. And a solenoid to be pressed.

In the valve body, a plurality of ports communicating with the advance hydraulic chamber, the retard hydraulic chamber, and the like are formed through the peripheral wall along the radial direction. On the other hand, in the sleeve, the plurality of communication passages are formed along the axial direction in the axial direction of the outer peripheral surface, and a plurality of communication holes are formed in the end portions and peripheral walls in the axial direction of the communication passages. Yes.

The spool valve slides in the axial direction by a control current output from the control unit to the solenoid, and controls each communication hole of the sleeve and the opening area of the communication hole via an oil hole formed in the peripheral wall. It is like that.

Then, by moving the spool valve in the axial direction according to the engine operation state, the communication passage and each port are appropriately communicated, so that the oil pumped from the oil pump is retarded from the advance hydraulic chamber of the vane rotor. The hydraulic chamber is selectively supplied and discharged to change the relative rotational phase of the camshaft with respect to the crankshaft.

US 7,389,756 B2

However, in the hydraulic control valve described in Patent Document 1, in order to improve the degree of freedom of the layout in the axial direction of each port of the body body, a plurality of communication paths along the axial direction are provided on the outer surface of the sleeve. In addition, a communication hole communicating with the port is formed at an axial end portion of the communication path, and a spool valve is slidably provided inside the sleeve. In addition to being complicated, it is necessary to form a communication path in the sleeve, and to ensure the slidability of the spool valve on the inner peripheral surface of the sleeve, so that high dimensional accuracy is required for the sleeve. As a result, the manufacturing work cost is inevitably increased.

An object of the present invention is to provide a hydraulic control valve that does not require high dimensional accuracy of components while improving the degree of freedom of the layout in the axial direction of the port.

The invention according to claim 1 is provided with a cylindrical valve body in which a plurality of ports through which hydraulic fluid flows in the radial direction of the peripheral wall is formed, and is slidable in the axial direction inside the valve body. A cylindrical shape in which a plurality of communication holes communicating with the plurality of ports are formed along the radial direction according to the sliding position, and a communication path communicating with each communication hole is formed along the inner axial direction. And a partition member that is housed and fixed in the inner axial direction of the spool valve and partitions the communication passage into a plurality of passage portions from the radial direction.

According to the present invention, it is possible to reduce the manufacturing cost because high dimensional accuracy of the component parts is not required while improving the degree of freedom of the layout in the axial direction of the port.

1 is an overall configuration diagram showing a cross section of a valve timing control apparatus to which a hydraulic control valve according to the present invention is applied. It is a front view which shows the state by which the vane rotor provided to this embodiment was hold | maintained in the rotation position of the intermediate phase. It is a perspective view which decomposes | disassembles and shows each components, such as a valve body of the electromagnetic switching valve provided for this embodiment. It is a side view which shows the valve body side of the electromagnetic switching valve provided for this embodiment. FIG. 5 is a sectional view taken along line AA in FIG. 4. It is a front view of the valve body provided for this embodiment. 6 is a longitudinal sectional view on the valve body side showing a state in which the spool valve of the electromagnetic switching valve provided in the present embodiment has moved to the maximum rightward position, where A is a sectional view taken along line BB in FIG. FIG. 6 is a sectional view taken along line CC of FIG. 6 is a longitudinal sectional view on the valve body side showing a state in which the spool valve of the electromagnetic switching valve provided in the present embodiment has moved to an intermediate position in the axial direction, where A is a sectional view taken along line BB in FIG. FIG. 6 is a sectional view taken along line CC of FIG. 6 is a longitudinal sectional view on the valve body side showing a state where the spool valve of the electromagnetic switching valve provided in the present embodiment has moved to the maximum leftward position, where A is a sectional view taken along line BB in FIG. FIG. 6 is a sectional view taken along line CC of FIG.

Hereinafter, an embodiment in which a hydraulic control valve according to the present invention is applied to a valve timing control device for an internal combustion engine will be described with reference to the drawings.

As shown in FIGS. 1 and 2, the valve timing control device is arranged along a longitudinal direction of the engine, and a sprocket 1 that is a driving rotary body that is rotationally driven by a crankshaft of the engine via a timing chain (not shown). And is arranged between the intake side camshaft 2 provided so as to be rotatable relative to the sprocket 1 and between the sprocket 1 and the camshaft 2, and converts the relative rotational phase of the both 1 and 2. A phase changing mechanism 3, a lock mechanism 4 that locks the phase changing mechanism 3 at the most retarded phase position, and a hydraulic circuit 5 that operates the phase changing mechanism 3 and the lock mechanism 4 independently of each other. Yes.

The sprocket 1 is formed in a substantially thick disk shape, has a gear portion 1a around which the timing chain is wound, and is configured as a rear cover that closes a rear end opening of the housing described later. In the center, a support hole 1b through which the one end 2a of the camshaft 2 is rotatably supported is formed.

The camshaft 2 is rotatably supported by a cylinder head 01 via a plurality of cam bearings 02, and a plurality of egg-shaped rotary cams for opening an intake valve, which is an unillustrated engine valve, are shafts on the outer peripheral surface. A bolt hole 6 into which a cam bolt 50 to be described later is screwed is formed in the direction of the internal axis of the one end portion 2a.

The bolt hole 6 is formed along the internal axial direction from the distal end side of the one end portion 2a, and is formed to have a stepped diameter from the opened front end side toward the inner bottom portion. A large diameter portion 6a having a diameter, a stepped portion 6b formed in a tapered shape from the rear end of the large diameter portion 6a, and a female screw portion 6c formed from the rear end to the rear end portion of the stepped portion 6b. And is composed of.

As shown in FIGS. 1 and 2, the phase change mechanism 3 includes a housing 7 that is integrally provided on the sprocket 1 in the axial direction, and a later-described valve body that becomes a cam bolt at one end 2 a of the camshaft 2. A vane rotor 9 which is a driven rotating body fixed in an axial direction through 50 and rotatably accommodated in the housing 7 and an operation chamber inside the housing 7 are arranged on an inner peripheral surface of a housing body 7a described later. There are provided a retarded hydraulic chamber 11 and an advanced hydraulic chamber 12 which are a retarded working chamber and an advanced working chamber, respectively, which are separated by four protruding shoes 10 and the vane rotor 9.

The housing 7 includes a cylindrical housing body 7a integrally formed of sintered metal, a front cover 13 that is formed by press molding and closes the front end opening of the housing body 7a, and a rear cover that closes the rear end opening. It is comprised from the said sprocket 1 which is. The housing body 7a, the front cover 13, and the sprocket 1 are fastened and fixed together by four bolts 14 that pass through the bolt insertion holes 10a of the shoes 10. The front cover 13 has a relatively large-diameter insertion hole 13a formed through the center thereof, and seals the inside of each

hydraulic chamber

11, 12 with the outer peripheral side inner peripheral surface of the insertion hole 13a. .

The vane rotor 9 is integrally formed of a metal material, and has a rotor portion 15 fixed to one end portion 2a of the camshaft 2 by a valve body 50; It consists of four vanes 16a to 16d projecting radially at the interval positions.

The rotor portion 15 is formed in a cylindrical shape having a relatively large diameter, and has a bolt insertion hole 15a continuous with the female screw hole 6c of the camshaft 2 in the central internal axial direction. The tip end surface of the one end portion 2a of the shaft 2 is in contact.

On the other hand, each of the vanes 16a to 16d is formed with a relatively short protruding length, and is disposed between the shoes 10 and has a circumferential width that is set to be substantially the same. It is formed in a plate shape.

Seal members

17a and 17b for sealing between the inner peripheral surface of the housing body 7a and the outer peripheral surface of the rotor portion 15 are provided on the outer peripheral surfaces of the vanes 16a to 16d and the tips of the shoes 10, respectively. .

As the vane rotor 9 rotates relative to the retard side as shown by a one-dot chain line in FIG. 2, the projecting surface 10b formed on the opposing side surface of the one shoe 10 that the one side surface of the first vane 16a faces. The rotational position on the maximum retarding angle side is regulated in contact with. In addition, as shown by a two-dot chain line in FIG. 2, when the relative rotation is performed toward the advance angle side, the other side surface of the first vane 16a is in contact with the opposite side surface 10c of the other shoe 10 and the maximum advance angle side rotation is performed. The position is regulated.

At this time, the other vanes 16b to 16d are in a separated state without coming into contact with the facing surfaces of the shoes 10 whose both side surfaces face each other in the circumferential direction. Therefore, the contact accuracy between the vane rotor 9 and the shoe 10 is improved, and the supply speed of hydraulic pressure to each of the

hydraulic chambers

11 and 12 to be described later is increased, and the forward / reverse rotation response of the vane rotor 9 is increased.

The retard hydraulic chambers 11 and the advance hydraulic chambers 12 described above are defined between both side surfaces of the vanes 16a to 16d in the forward / reverse rotation direction and both side surfaces of the shoes 10, respectively. The angle hydraulic chamber 11 and each advance hydraulic chamber 12 are respectively connected to a hydraulic circuit 5 described later via a retard side communication passage 11a and an advance side communication passage 12a formed substantially radially inside the rotor portion 15. Communicating with

The lock mechanism 4 holds the vane rotor 9 at the most retarded angle rotation position (the one-dot chain line position in FIG. 2) with respect to the housing 7.

That is, as shown in FIGS. 1 and 2, the lock mechanism 4 includes a lock hole constituting portion 1c (described only in FIG. 1) that is press-fitted and fixed at a predetermined position on the inner peripheral side of the sprocket 1, and the lock hole. The lock hole 24 formed in the component 1c and the sliding hole 27 formed in the inner axial direction of the first vane 16a having the maximum width of the vane rotor 9 are provided so as to be capable of moving forward and backward, and a small-diameter distal end portion 25a is provided. A lock pin 25 that engages and disengages with each lock hole 24, a coil spring 26 that urges the lock pin 25 toward the lock hole 24, and the lock pin 25 that is formed inside the lock hole 24 and that is supplied with hydraulic pressure. 25, a release pressure receiving chamber (not shown) that releases the engagement by retreating each lock hole 24 against the spring force of the coil spring 26, and a lock passage for supplying hydraulic pressure to the release pressure receiving chamber , It is composed mainly from.

The lock hole 24 is formed in a circular shape having a diameter sufficiently larger than the outer diameter of the small-diameter tip portion 25a of the lock pin 25, and the rotation of the inner side surface of the sprocket 1 on the most retarded side of the vane rotor 9 is performed. It is formed at a position corresponding to the position.

The lock pin 25 is moved backward by receiving the hydraulic pressure supplied to the pressure receiving chamber for release on the pressure receiving surface of the tip portion 25a, and the tip portion 25a is moved by the spring force of the coil spring 26 provided on the rear end side. The vane rotor 9 is locked into the housing 7 by engaging with the lock hole 24.

Further, the release pressure receiving chamber is supplied with the same hydraulic pressure as that supplied to the retard hydraulic chamber 11, and the lock pin 25 is moved backward against the spring force of the coil spring 26 by this hydraulic pressure. It is like that.

As shown in FIGS. 1 and 2, the hydraulic circuit 5 includes a retard passage 18 for supplying and exhausting hydraulic pressure to and from each retard hydraulic chamber 11 via a retard communication passage 11a, and each advance hydraulic pressure. An advance passage 19 for supplying and discharging hydraulic pressure to and from the chamber 12 via the advance side communication passage 12a, the lock passage for supplying and discharging hydraulic pressure to and from the release pressure receiving chamber, and the respective retard and advance angles An oil pump 20 that selectively supplies hydraulic oil to the

passages

18 and 19, and a single electromagnetic switching valve that is a hydraulic control valve that switches between the retard passage 18 and the advance passage 19 according to the engine operating state. 21.

One end of each of the retard passage 18 and the advance passage 19 is connected to a retard port 18a and an advance port 19a of a valve body 50, which will be described later, of the electromagnetic switching valve 21, while the other end is disposed on the other end side. The retard

angle advance chambers

11a and 12a communicate with the retard angle hydraulic chambers 11 and the advance angle hydraulic chambers 12 respectively.

The lock passage communicates with the retard passage 18 so that the hydraulic pressure supplied to and discharged from the retard hydraulic chamber 11 is supplied to and discharged from the release pressure receiving chamber.

The oil pump 20 is a general one such as a trochoid pump that is rotationally driven by an engine crankshaft, and hydraulic oil sucked from the oil pan 23 through the suction passage 20b by rotation of the outer and inner rotors. It is discharged through the discharge passage 20a, a part of which is supplied from the main oil gallery M / G to each sliding part of the internal combustion engine, and the other is supplied to the electromagnetic switching valve 21 side. ing. In addition, a filtration filter (not shown) is provided on the downstream side of the discharge passage 20a, and excess hydraulic oil discharged from the discharge passage 20a is returned to the oil pan 23 through the drain passage 22 to be appropriate. A non-illustrated flow rate control valve for controlling the flow rate is provided.

As shown in FIG. 1 and FIG. 3, the electromagnetic switching valve 21 is a three-port, three-position proportional valve, and slides in a bottomed cylindrical valve body 50 and an internal axis direction of the valve body 50. A cylindrical spool valve 51 provided movably, a columnar sleeve 52 that is a partition member inserted and fixed inside the spool valve 51, and a disk-like shape that is press-fitted into one end opening of the spool valve 51. The retainer 53, a valve spring 54 which is elastically mounted between the retainer 53 and the bottom surface of the valve body 50 and biases the spool valve body 51 in the right direction in FIG. A solenoid part 55, which is an actuator provided at one end of the valve body 50 and moves the spool valve 51 in the left direction in the figure against the spring force of the valve spring 54, is mainly constituted. It has been.

The valve body 50 is formed of a ferrous metal material and functions as a cam bolt as described above. As shown in FIGS. 1 and 4, the hexagonal head 50a on the solenoid part 55 side, and the head A cylindrical shaft portion 50b that extends in the axial direction from the base portion of 50a, and an outer diameter that is formed on the distal end side of the cylindrical shaft portion 50b and that opposes the reduced diameter step portion 6b of the camshaft 2 from the radial direction. A stepped tapered cone portion 50c, a small-diameter male screw portion 50d formed at the tip portion of the cone portion 50c and screwed into the female screw hole 6c of the camshaft 2, and an inner shaft from the tip surface side of the head portion 50a. The sliding hole 50e is formed mainly in the direction.

In the head 50a, an annular stopper 56 for restricting the maximum sliding position of the spool valve 51 toward the solenoid 55 is press-fitted and fixed to the inner peripheral surface of a large-diameter groove formed on the inner tip side. .

The cylindrical shaft portion 50b is provided with four retard ports 18a and advance ports 19a formed in the peripheral wall so as to penetrate each other along the cross radial direction.

The conical portion 50c has a step-conical introduction chamber 57 formed between the outer peripheral surface and the large-diameter portion 6a and the step portion 6b of the camshaft 2, and a portion of the peripheral wall near the cylindrical shaft portion 50b. An introduction port 58 communicating with the introduction chamber 57 is formed penetrating along the radial direction.

The spool valve 51 is made of an aluminum alloy material, and has a holding hole 59 that is a communication path through which the sleeve 52 is inserted and held in the inner axial direction. There are two

guide parts

51a, 51b and three first to

third land parts

51c, 51d, 51e which are provided between the two

guide parts

51a, 51b and have the same outer diameter. Further, a first groove groove 60 is formed on the outer peripheral surface between the one side guide portion 51a on the retainer 53 side and the first land portion 51c adjacent to the one guide portion 51a. In addition, a second groove groove 61 is formed between the first land portion 51c and the second land portion 51d adjacent thereto so as to communicate with the advance port 19a as appropriate. A third groove groove 62 is formed between the second land portion 51d and the third land portion 51e adjacent to the second land portion 51d. The third groove groove 62 communicates appropriately with the retard port 18a and the advance port 19a. Between the three land portions 51e and the other side guide portion 51b adjacent to the third land portion 51e, a fourth groove groove 63 communicating with the retard port 18a as appropriate is formed.

In the first to fourth groove grooves 60 to 63, the first communication hole 60a to the fourth communication hole 63a, which are always in communication with the holding hole 59 at predetermined angular positions in the circumferential direction, are radially formed on the respective bottom walls. Each is formed through. The first to fourth communication holes 60a to 63a are formed at predetermined angular positions in the circumferential direction of the groove grooves 60 to 63, and the first and third communication holes 60 and 62 are formed at substantially the same angular position. On the other hand, the second and fourth communication holes 61 and 63 are formed at an angular position of about 90 °.

In addition, a drain plug 64 is press-fitted and fixed to the open end of the spool valve 51 opposite to the retainer 53. The drain plug 64 is formed in a bottomed cylindrical shape, and the spool valve 51 is disposed at one end in the axial direction. An annular flange portion 64a that is press-fitted and fixed in one end opening of 51 is integrally provided, and a drain hole 64b is formed in the inner axial direction. In addition, a pair of opening holes 64c communicating with the drain hole 64b and the outside are formed at a substantially central position in the axial direction of the drain plug 64 along the radial direction.

The flange portion 64 a is press-fitted and fixed to one end opening portion of the spool valve 51, and cooperates with the retainer 53 to hold both end edges of the sleeve 52 from the axial direction to hold the sleeve 52 in the spool valve 51. The movement in the axial direction is regulated.

As shown in FIGS. 3 and 5, the sleeve 52 is integrally formed of a synthetic resin material in an elongated rod shape, and the outer peripheral surfaces of both

axial end portions

52a and 52b formed in a cylindrical shape are held by the spool valve 51. The hole 59 is inserted into and fixed to the inner peripheral surface of the hole 59 through a small clearance or by fitting with a gap, and between the both

end portions

52a and 52b, four first to fourth four partition walls 52c having a substantially cross-shaped cross section are provided. It is partitioned into fourth passage portions 65a to 65d.

As shown in FIG. 5, each of the passage portions 65a to 65d is formed in a substantially V-shaped cross section by the partition wall 52c, and is formed long along the axial direction between the both

end portions

52a and 52b. ing. Further, both end portions in the axial direction of the first passage portion 65a and the second passage portion 65b formed in an axially symmetric position with the first passage portion 65a are closed by the built-up portions 52d. On the other hand, the third passage portion 65c and the fourth passage portion 65d that is axially symmetric with the third passage portion 65c have a pair of

discharge holes

66a and 66b at both ends in the axial direction. The discharge hole 66a on the end side always communicates with the drain hole 64b of the drain plug 64.

Each of the passage portions 65a to 65d appropriately communicates with the fourth communication hole 63a of the fourth groove groove 63 on the retard passage 18 side according to the axial sliding position of the spool valve 51. The second communication groove 61a of the second groove groove 61 on the advance angle passage 19 side communicates with the second communication hole 61a as appropriate.

The retainer 53 is press-fitted and fixed to the inner peripheral surface of the open end of the one end portion 51a of the spool valve 51, and a through hole 53a is formed through the center of the retainer 53.

As shown in FIG. 1, the solenoid portion 55 includes a solenoid casing 71 fixed to a chain cover (not shown) with a bolt 70 via a bolt 70, and is housed and held inside the solenoid casing 71, so as to control the engine. (ECU) A coil 72 from which a control current is output from 37, a cylindrical fixed yoke 73 fixed to the inner peripheral side of the coil 72, and an axially slidable inside the fixed yoke 73 The movable plunger 74 is integrally formed with the distal end portion of the movable plunger 74, and the distal end portion 75 a abuts against the drain plug 64 in the axial direction, and resists the spring force of the valve spring 54. 1 mainly includes a drive rod 75 that presses 51 in the left direction in FIG.

The solenoid casing 71 is held in the holding hole of the chain cover by a seal ring 76, and a synthetic resin connector 77 having a terminal 78 electrically connected to the ECU 37 at the rear end side. Is attached.

As shown in FIGS. 7 to 9, the solenoid unit 55 moves the spool valve 51 to three positions in the front-rear axis direction by the relative pressure between the control current of the ECU 37 and the valve spring 54, and The spool valve 51 communicates with the second groove groove 61 to the fourth groove groove 63 (second communication hole 61a to fourth communication hole 63a) and the retardation port 18a and the advance port 19a corresponding to the radial groove in the radial direction. Alternatively, the open ends of the retard port 18a and the advance port 19a are closed by the land portions 51c to 51e to block communication.

The first groove groove 60 and the introduction port 58 are always in communication at any sliding position of the spool valve 51. Therefore, the hydraulic pressure discharged from the oil pump 20 is introduced from the introduction chamber 57 to the introduction port 58. The first groove groove 60 (first communication hole 60a) is always supplied into the first and

second passage portions

65a and 65b of the sleeve 52.

In the ECU 37, an internal computer detects a crank angle sensor (engine speed detection), an air flow meter, an engine water temperature sensor, an engine temperature sensor, a throttle valve opening sensor, and a current rotation phase of the camshaft 2 which are not shown. Information signals from various sensors such as a cam angle sensor are input to detect the current engine operating state, and as described above, a control current is output to the coil 72 of the electromagnetic switching valve 21 or the current supply is cut off. Thus, the movement position of the spool valve 51 is controlled to selectively switch the ports.
[Operation of this embodiment]
Hereinafter, a specific operation of the valve timing control device of this embodiment will be described.

First, for example, when the engine is stopped by turning off the ignition switch, the energization to the solenoid unit 55 is also cut off, so that the spool valve 51 has a spring force of the valve spring 54 as shown in FIG. Is held at the maximum rightward position (first position). At this time, the advance port 19a of the valve body 50 is communicated with the second groove groove 61 (second communication hole 61a) of the spool valve 51 by the spool valve 51, and the third and fourth passage portions 65c of the sleeve 52 are communicated. , D are communicated (see FIG. 7A). At the same time, the introduction port 58 communicates with the first groove groove 60 (first communication hole 60a), the first and

second passage portions

65a and 65b, and the

passage portions

65a and 65b and the retardation port 18a. Communication is made (see FIG. 7B).

Therefore, as shown by the arrow in FIG. 7A, the hydraulic oil in the advance hydraulic chamber 12 passes through the second communication hole 61a from the advance port 19a and is discharged from the third and

fourth passage portions

65c and 65d. It is discharged to the outside through the drain hole 64b and the opening hole 64c of the drain plug 64 through 66a. Thereby, the inside of each advance hydraulic chamber 12 becomes a low pressure.

When the engine is stopped, the oil pump 20 is also stopped, so that no hydraulic pressure is supplied to the retard / advance

hydraulic chambers

11 and 12, so that the vane rotor 9 is connected to the camshaft 2. Due to the negative alternating torque acting, as shown by the one-dot chain line in FIG. 2, the sprocket 1 rotates relative to the counterclockwise direction (most retarded angle direction). Therefore, the intake valve is controlled so that the valve timing is the most retarded phase.

At this time, when the vane rotor 9 is held at the most retarded position, the lock pin 25 is advanced by the spring force of the coil spring 26 and is engaged with the lock hole 24 so that the vane rotor 9 is locked to the housing 7. It becomes a state.

Next, when the engine is started by turning on the ignition switch, the oil pump 20 is also driven, and the hydraulic pressure discharged from the oil pump 20 is changed to the introduction port as shown by the arrow in FIG. 7B. 58 flows into the first and

second passage portions

65a and 65b through the first communication holes 60a, and from there through the third communication holes 62a, the retard ports 18a, and the retard communication passages 11a. Supplied to the angular hydraulic chamber 11, each retarded hydraulic chamber 11 is in a high pressure state. Accordingly, since the vane rotor 9 is maintained in the state of relative rotation to the most retarded position, the valve timing of the intake valve is controlled to the retard side. Therefore, the engine startability is improved.

At this time, the same hydraulic pressure as that of the retarded hydraulic chamber 11 is supplied to the release pressure receiving chamber through the lock passage. However, since the hydraulic pressure in the release pressure receiving chamber does not increase at the initial stage of cranking, The pin 25 is engaged with the lock hole 24 and locked. Therefore, flapping of the vane rotor 9 due to the alternating torque can be suppressed.

Thereafter, when the hydraulic pressure supplied to the release pressure receiving chamber via the lock passage becomes high, the lock pin 25 is moved backward against the spring force of the coil spring 26 to release the lock state with the lock hole 24. As a result, the vane rotor 9 becomes free.

Next, when the engine shifts from, for example, an idling operation to a steady operation, a predetermined amount of current is supplied from the ECU 37 to the coil 72 of the solenoid unit 55. As a result, the spool valve 51 is slightly moved in the left direction in the drawing against the spring force of the valve spring 54 as shown in FIG. 8 by the pressing force of the drive rod 75 (second position). In this state, the retard port 18a and the advance port 19a are closed by the second and

third land portions

51d and 51e, and the second groove groove 61 and the third groove groove 62 are closed by the inner peripheral surface of the valve body 50. To do.

Therefore, as shown in FIG. 8A, each of the retarded hydraulic chamber 11 and the advanced hydraulic chamber 12 has no hydraulic oil discharged from the inside thereof, and at the same time, the hydraulic fluid pumped from the oil pump 20 As shown in FIG. 8B, the supply to the

hydraulic chambers

11 and 12 is interrupted.

Therefore, the vane rotor 9 is held at an intermediate position between the most retarded angle and the most advanced angle, as shown by the solid line in FIG. Therefore, the valve timing of the intake valve is controlled to an intermediate phase between the most retarded angle and the most advanced angle, so that the engine rotation can be stabilized and fuel consumption can be improved during steady operation.

Next, for example, when the engine shifts from a steady operation to a high rotation / high load region, a larger current is supplied from the ECU 37 to the coil 72 of the solenoid unit 55, and the spool valve 51 is moved by the pressing force of the drive rod 75. As shown in FIG. 9, the valve spring 54 moves to the left in the maximum direction against the spring force (third position). Accordingly, the retard port 18a communicates with the fourth groove groove 63 (fourth communication hole 63a) and also communicates with the third and

fourth passage portions

65c and 65d.

On the other hand, the introduction port 58 and the first groove groove 60 (first communication hole 60a) communicate with each other, and the first communication hole 60a communicates with the first and

second passage portions

65a and 65b and the advance port 19a.

Accordingly, as shown by the arrow in FIG. 9A, the hydraulic pressure in each retarded hydraulic chamber 11 passes through the fourth communication hole 63a, the third and

fourth passage portions

65c, 65d from the retard port 18a, and the discharge hole 66a. The water is discharged to the outside through the drain hole 64b and the opening hole 64c. For this reason, the inside of each retarded hydraulic chamber 11 becomes a low pressure. On the other hand, the hydraulic fluid pumped from the oil pump 20 to each advance hydraulic chamber 12 passes through the first passage hole 60a, the first and

second passage portions

65a, 65b, etc., as indicated by arrows in FIG. 9B. When supplied, each advance hydraulic chamber 12 becomes high pressure.

Therefore, the vane rotor 9 rotates in the clockwise direction and relatively rotates to the maximum advance side, as indicated by the two-dot chain line in FIG. As a result, the valve timing of the intake valve becomes the most advanced angle phase, the valve overlap of the exhaust valve increases, the intake charging efficiency increases, and the output torque of the engine can be improved.

As described above, the ECU 37 controls the movement of the spool valve 51 in the axial direction by energizing or shutting off the electromagnetic switching valve 21 with a predetermined energization amount in accordance with the operating state of the engine, thereby controlling the first position. Control to the third position. As a result, the phase change mechanism 3 and the lock mechanism 4 are controlled to control the camshaft 2 to the optimum relative rotational position with respect to the sprocket 1, so that the valve timing control accuracy can be improved.

As described above, in the present embodiment, the spool valve 51 is slidably provided in the valve body 50, and the sleeve 52 having a relatively simple passage portion is fixed inside the spool valve 51. The entire structure of the switching valve 21 can be simplified.

Further, since the sleeve 52 is merely fixed in the spool valve 51, high dimensional accuracy is not required for the sleeve 52, so that the manufacturing work cost can be reduced also in this respect.

Moreover, the sleeve 52 does not require the high dimensional accuracy and can be formed of a synthetic resin material, so that the weight of the electromagnetic switching valve 21 can be reduced.

Further, since the metal spool valve 51 and the synthetic resin sleeve 52 have different coefficients of thermal expansion, when the temperature of the hydraulic oil (engine oil) is low at the time of cold start, for example, Although the clearance between 51 and 52 increases, when the temperature becomes higher than a predetermined temperature during steady operation, the thermal expansion coefficient on the sleeve 52 side increases and the clearance decreases. That is, the outer peripheral surfaces of both

end portions

52a and 52b of the sleeve 52 and the outer end surfaces of the four cross-shaped partition walls 52c are in close contact with the inner peripheral surface of the spool valve 51, thereby reducing the clearance.

Therefore, oil leakage between the two systems in the spool valve 51, that is, oil leakage between the two systems of the first and

second passage portions

65a and 65b and the third and

fourth passage portions

65c and 65d is sufficiently suppressed. It becomes possible.

As a result, an excessive dimensional tolerance of the sleeve 52 with respect to the inner peripheral surface of the spool valve 51 is not required, so that the degree of freedom in the axial layout of the groove grooves 60 to 63 of the spool valve 51 is improved and the manufacturing is performed. Cost can be reduced.

Further, the first passage portion 65a and the second passage portion 65b partitioned by the sleeve 52, and the third passage portion 65c and the fourth passage portion 65d are respectively formed at axially symmetric positions, and these first and second passage portions are formed. Since the hydraulic pressure flowing through the

passage portions

65a and 65b is for supply and the hydraulic pressure flowing through the third and

fourth passage portions

65c and 65d is for discharge and the hydraulic pressure is of the same system, it acts on the sleeve 52. You can balance the pressure.

Further, due to the unique configuration of the valve body 50, the axial length of the bolt hole 6 of the one end portion 2a of the camshaft 2 can be shortened. For this reason, it is possible to suppress a decrease in rigidity on the one end 2a side of the camshaft 2, and in particular, it is possible to suppress a decrease in torsional rigidity.

Thereby, the support rigidity with respect to the vane rotor 9 is also increased, stable support is possible, and the rotation transmission from the vane rotor 9 to the camshaft 2 is also improved.

Furthermore, drilling of the camshaft 2 is facilitated by shortening the axial length of the bolt hole 6 and simplifying the longitudinal sectional shape.

Further, since the valve body 50 is formed such that the outer diameter of the tip end portion (conical portion 50c) is smaller than the inner diameter of the bolt hole 6 of the camshaft 2, the introduction chamber 57 and the like are formed using this space portion. It becomes possible to do. For this reason, the flow path structure comprised by the said introduction chamber 57, the introduction port 58, etc. can be simplified.

Further, in the present embodiment, the single electromagnetic switching valve 21 performs two functions for controlling the hydraulic pressure to the retard hydraulic chamber 11 and the advanced hydraulic chamber 12 and controlling the hydraulic pressure to the release pressure receiving chamber. Therefore, the degree of freedom of layout on the engine body is improved and the cost can be reduced.

Furthermore, since each passage hole is closed by the sliding position of the spool valve 51 of the electromagnetic switching valve 21 and the vane rotor 9 is held at the intermediate phase position, this holding property is improved.

The present invention is not limited to the configuration of the above embodiment, and the case where the hydraulic control valve is applied to a valve timing control device has been shown. However, other than the valve timing control device, for example, an automatic transmission of a vehicle, etc. It is also possible to apply to other devices.

Also, it is possible to use an oil pressure other than the electromagnetic force of the solenoid unit 55 as an actuator.

Furthermore, the valve timing control device can be applied not only to the intake side but also to the exhaust side.

It is possible to form the spool valve 51 from an iron-based metal and the sleeve 52 from an aluminum alloy material.

In the sleeve 52, the holding hole 59 of the spool valve 51 is divided into four first to fourth passage portions 65a to 65d by the four partition walls 52c having a substantially cross-shaped cross section as described above. If the holding hole 59 is divided into at least two passage portions by the sleeve 52, the hydraulic pressure can be supplied to and discharged from the

hydraulic chambers

11 and 12, respectively.

Claims

A cylindrical valve body having a plurality of ports penetrating the working fluid in the radial direction of the peripheral wall;
A plurality of communication holes are provided in the valve body so as to be slidable in the axial direction and communicate with the plurality of ports according to the sliding position along the radial direction. A cylindrical spool valve in which a communication passage communicating therewith is formed along the internal axial direction;
A partition member that is housed and fixed in the communication passage of the spool valve and partitions the communication passage into a plurality of passage portions along the axial direction;
A hydraulic control valve comprising:
The hydraulic control valve according to claim 1,
The hydraulic control valve, wherein the partition member is formed of a material having a thermal expansion coefficient larger than that of the spool valve.
The hydraulic control valve according to claim 2,
The partition valve is formed of a synthetic resin material, whereas the spool valve is formed of a metal material.
The hydraulic control valve according to claim 3,
The hydraulic control valve, wherein the partition member is fixed inside the spool valve by press-fitting or clearance fitting.
The hydraulic control valve according to claim 4,
The spool control valve is formed in a cylindrical shape, and is a hydraulic control valve.
The hydraulic control valve according to claim 2,
The spool valve is formed of an iron-based metal material, and the partition member is formed of an aluminum alloy material.
The hydraulic control valve according to claim 1,
Each passage portion of the communication passage is formed at a radially symmetrical position around the axis of the partition member, and the same system of hydraulic fluid flows through each of the passage portions formed at the symmetrical position. Hydraulic control valve characterized by
The hydraulic control valve according to claim 7,
The hydraulic control valve, wherein the communication passage is partitioned into four passage portions by a pair of supply passage portions and discharge passage portions of the same system by the partition member.
The hydraulic control valve according to claim 8,
The hydraulic control valve according to claim 1, wherein the partition member has a substantially cross-shaped cross section.
The hydraulic control valve according to claim 9,
The hydraulic control valve according to claim 1, wherein a drain hole is formed on the axial end portion side of the partition member to communicate with the pair of communication passages arranged to face each other in the radial direction.
The hydraulic control valve according to claim 10,
The hydraulic control valve according to claim 1, wherein the drain hole is formed in a thick portion formed thicker than a width in a width direction of the cross wall of the partition member.
The hydraulic control valve according to claim 1,
A hydraulic control valve, wherein the hydraulic fluid is arranged and formed so as to be introduced from one end side in the axial direction of the spool valve and discharged from the other end side.
The hydraulic control valve according to claim 1,
The hydraulic control valve, wherein the communication passage is partitioned into two passage portions in a radial direction by the partition member.
A hydraulic control valve used in a valve timing control device of an internal combustion engine that operates a movable member by selectively supplying and discharging hydraulic oil to convert a relative rotational phase of a camshaft with respect to a crankshaft,
The hydraulic control valve is
A hollow cam bolt in which the movable member is fixed to the axial end portion of the camshaft, and a supply / discharge port through which hydraulic oil flows in the radial direction of the peripheral wall is formed,
A cylindrical spool valve that is slidable in the internal axial direction of the cam bolt and communicates or blocks a plurality of communication holes formed in a peripheral wall and the supply / exhaust port according to a sliding position;
A partition member that is housed and fixed along the internal axial direction of the spool valve and partitions the inside of the spool valve into a plurality of communication passages that can communicate with the communication holes from the radial direction;
A hydraulic control valve comprising:
The hydraulic control valve according to claim 14,
A gap passage is formed between the inner peripheral surface of the bolt insertion hole of the camshaft and the outer peripheral surface of the cam bolt to introduce hydraulic oil pumped from an oil pump into the cam bolt. Hydraulic control valve.
A driving rotor in which a rotational force is transmitted from the crankshaft and an operation chamber is formed inside;
The camshaft is fixed to one end of the camshaft in the axial direction, and is rotatably accommodated in the drive rotating body to separate the working chamber into an advance working chamber and a retard working chamber. A driven rotating body that rotates relative to the advance side or the retard side with respect to the drive rotating body by supplying and discharging hydraulic oil;
A hydraulic control valve for controlling the supply and discharge of the hydraulic oil pumped from the oil pump to and from the two working chambers;
An actuator for operating the hydraulic control valve;
An internal combustion engine valve timing control apparatus comprising:
The hydraulic control valve is
A hollow cam bolt in which the driven rotor is fixed to the axial end of the camshaft, and a supply / discharge port through which hydraulic oil flows in the radial direction of the peripheral wall is formed,
A cylindrical spool valve that is slidable in the internal axial direction of the cam bolt and communicates or blocks a plurality of communication holes formed in a peripheral wall and the supply / exhaust port according to a sliding position;
And a partition member that is housed and fixed along the internal axial direction of the spool valve and partitions the interior of the spool valve into a plurality of communication passages that can communicate with the communication holes from the radial direction. A valve timing control device for an internal combustion engine.