CN103362589A

CN103362589A - A solenoid actuator for an internal combustion engine

Info

Publication number: CN103362589A
Application number: CN2013101140071A
Authority: CN
Inventors: 高桥裕也; 铃木康义
Original assignee: Denso Corp
Current assignee: Denso Corp
Priority date: 2012-04-06
Filing date: 2013-04-03
Publication date: 2013-10-23
Also published as: JP2013217265A; DE102013206016A1

Abstract

The invention discloses a solenoid actuator for an internal combustion engine. A distal end portion (64) of restriction pins (60, 601, 602 ) can be engaged with engaging grooves (14, 24) of a slider (21), when the restriction pins (60, 601, 602 ) are moved in a forward direction. A plunger (50) has an end portion with which the restriction pins (60, 601, 602) are fixedly connected. A permanent magnet (41) is held stationary at a corresponding position , which is located on one side of the plunger (50) opposite to the distal end portion (64) of the restriction pins (60, 601, 602). The permanent magnet (41) exerts a magnetic attracting force for magnetically attracting an attraction surface (511) of the plunger (50) in a reverse direction which is opposite to the forward direction. When current flows through an coil (42), the coil (42) generates electromagnetic force to magnetically attract the plunger (50 ) in the forward direction so as to move the plunger (50) and the restriction pins (60, 601, 602) in the forward direction.

Description

The solenoid actuator that is used for internal-combustion engine

Technical field

The present invention relates to the solenoid actuator of a kind of valve stroke for internal-combustion engine (valve lift) controlling device.

Background technique

Formerly in the valve stroke controlling device of one lift in the suction valve of known adjusting internal-combustion engine and the outlet valve, known is the position that changes slide block (slider), and this slide block can and can move with respect to this camshaft along the axial direction of this camshaft with the rotation of integrated camshaft ground.In addition, in known solenoid actuator, drive banking pin by electromagnetic force, the distal portion of banking pin and the engaging groove that is formed at this slide block are meshed.For example, US6,967,550B2 have instructed a kind of solenoid actuator, and it drives the repulsive force between the electromagnetic force that produces when banking pin passes the magnetic force of permanent magnet and coil electricity.

At US6, in the solenoid actuator of 967,550B2, to being sandwiched in that two permanent magnets between the dish drive so that itself and banking pin are mobile integratedly.Therefore, when driving permanent magnet, permanent magnet may owing to producing to shake when driving permanent magnet and rupture (or breaking), may cause solenoid actuator to be in not operable state thus.For overcoming such shortcoming, it is contemplated that the thickness of slab of increase dish is to improve shock resistance.Yet the increase of the thickness of slab of dish can cause that the weight of the moveable part of solenoid actuator increases, thereby may cause the motion speed of solenoid actuator to descend.

Summary of the invention

Made in view of the foregoing the present invention.Therefore, an object of the present invention is to provide a kind of solenoid actuator of the valve stroke controlling device for internal-combustion engine, the applying of vibrations that it produces in the time of can effectively limiting and be worked by solenoid actuator and cause the fracture of permanent magnet.

According to the present invention, provide a kind of solenoid actuator for the valve stroke controlling device, the lift amount of one of the suction valve of its adjusting internal-combustion engine and outlet valve.Described solenoid actuator comprises banking pin, plunger, permanent magnet, coil and spring.Described banking pin be configured to towards with engaging groove to-and-fro motion away from slide block, described slide block can and can move with respect to described camshaft along the axial direction of described camshaft with the integrated camshaft ground rotation of described valve stroke controlling device.When described banking pin along forward direction when the described engaging groove of described slide block moves, the distal portion of described banking pin can with the described engaging groove engagement of described slide block.When the torque that applies from described camshaft when described banking pin utilization is moved away from the engaging groove of described slide block along the backward directions opposite with described forward direction, the described engaging groove disengaging of the described distal portion of described banking pin and described slide block.Described plunger is made by magnetic material and is had an end that is fastenedly connected with described banking pin.Described permanent magnet is static to remain on corresponding position, and corresponding position is positioned at a side relative with described distal portion described banking pin described plunger.Described permanent magnet applies magnetic attraction magnetically to attract the suction surface of described plunger on described backward directions.To described coil electricity the time, described coil produces electromagnetic force, magnetically attracting described plunger on described forward direction, thereby moves described plunger along described forward direction.Described spring promotes described banking pin and described plunger along described forward direction.

Description of drawings

Accompanying drawing described herein only is used for the purpose of explanation, is not to be intended to limit the scope of the invention by any way.

Fig. 1 is the schematic diagram that has according to the valve stroke controlling device of the solenoid actuator of the embodiment of the invention, its show begin from little lift state to the high-lift state cutting for operation the time serviceability;

Fig. 2 is the sectional view along Fig. 1 center line II-II;

Fig. 3 is the schematic diagram of valve stroke controlling device with solenoid actuator of the present embodiment, its show from little lift state to the high-lift state cutting for operation middle the time serviceability;

Fig. 4 is the sectional view along Fig. 3 center line IV-IV;

Fig. 5 is the schematic diagram of valve stroke controlling device with solenoid actuator of the present embodiment, its show begin from the high-lift state to little lift state cutting for operation the time serviceability;

Fig. 6 is the sectional view along Fig. 5 center line VI-VI;

Fig. 7 is the sectional view of the solenoid actuator of the present embodiment, and it shows the most backward position of plunger and banking pin;

Fig. 8 is the partial enlarged drawing of regional VIII among Fig. 7;

Fig. 9 is the local amplification sectional view of regional IX among Fig. 7;

Figure 10 is the sectional view of the solenoid actuator of the present embodiment, and it shows the forward facing position of plunger and banking pin;

Figure 11 is the schematic diagram of power of plunger that is applied to the solenoid actuator of the present embodiment under the coil non-power status; And

Figure 12 is the schematic diagram of power of plunger that is applied to the solenoid actuator of the present embodiment under the coil "on" position.

Embodiment

Will embodiment of the invention will be described with reference to drawings.

The solenoid actuator of the present embodiment is applied to regulate the valve stroke controlling device of amount (being also referred to as lift amount) of lift of each suction valve of internal-combustion engine.

Referring now to Fig. 1 to 6 the valve stroke controlling device is described.

Shown in Fig. 1 to 6, valve stroke controlling device 10 is regulated each

suction valve

91,92 lift by a corresponding cam in the cam that is wholely set with slide block 21.Slide block 21 can rotate integratedly with camshaft 11 and can move with respect to camshaft 11 along the axial direction of camshaft 11.Each

suction valve

91,92 by

corresponding roller

31,32 and

corresponding swing arm

33,34 be connected to corresponding cam.

Camshaft 11 is along the rotary synchronous ground rotation of preset rotating direction and bent axle (not shown).Can see from the left side of Fig. 1 (and Fig. 3 or Fig. 5), the sense of rotation of camshaft 11 is counterclockwise.

Shown in Fig. 2 (and Fig. 4 or Fig. 6), the external spline teeth (male spline tooth) that is formed on the outer circumferential face of camshaft 11 is suitable with the inner spline gear (female spline tooth) of slide block 21.In Fig. 1 (and Fig. 3 or Fig. 5), for simplicity, not shown external spline teeth.

Slide block 21 is configured to tubular, and the engagement of the external spline teeth of the inner spline gear of slide block 21 and camshaft 11, so that slide block 21 can rotate integratedly with camshaft 11 and can move with respect to camshaft 11 along the axial direction of camshaft 11.That is, in axial direction to-and-fro motion between two

slide block limiters

12,22 of slide block 21, each in two slide block limiters is configured to flange-shape and is fixed to camshaft 11.

Cut for

section

13,23,

little lift cams

18,28 and long-

nose cam

19,29 be formed on in two opposed ends of slide block 21 each, two opposed ends on the axial direction of camshaft 11 toward each other.Therefore, in the present embodiment, first group cut for section 13, little lift cams 18 and long-nose cam 19, and second group cut two opposed ends that are separately positioned on slide block 21 for section 23, little lift cams 28 and long-nose cam 29.Cut for

section

13,23 and be set to cut axial position for slide block 21 with respect to camshaft 11.

In the following description, be positioned at cutting of Fig. 1 left side and be called first for section 13 and cut for section 13, be positioned at cutting of Fig. 1 right side and be called second for section 23 and cut for section 23.Similarly, little lift cams 18 and long-nose cam 19 are called the first little lift cams 18 and first lift cams 19.Equally, little lift cams 28 and long-nose cam 29 are called the second little lift cams 28 and second largest lift cams 29.The structure of first and second groups of above-mentioned parts is basically mutually the same.Therefore, in the following description, only the structure of first group of parts (first cuts for section 13, the first little lift cams 18 and first lift cams 19) described.

First cuts for section 13 and has the first engaging groove 14.The first engaging groove 14 has front portion 15, transition part 16 and rear portion 17.

Front portion 15 is spaced apart from each other at the axial direction of camshaft 11 with rear portion 17, and along extending with the axial vertical direction of camshaft 11.As shown in Figure 2, the degree of depth of anterior 15 radial groove is along slide block 21(and camshaft 11) sense of rotation (side) reduces to the front side.In addition, as shown in Figure 6, the degree of depth of the radial groove at rear portion 17 is along slide block 21(and camshaft 11) sense of rotation reduce to rear side (tail side).

Transition part 16 is connected between front portion 15 and the rear portion 17, and tilt, so that a side of transition part 16 (namely, side along sense of rotation) moves closer to anterior 15 along the direction vertical with the axial direction of camshaft 11, and so that the tail side of transition part 16 the tail side of sense of rotation (that is, along) moves closer to rear portion 17 along the direction vertical with the axial direction of camshaft 11.

Valve stroke controlling device 10 has two and is arranged at respectively first and cuts for section 13 and second and cut solenoid actuator 401,402 for section 23.

Drive banking pin 601 corresponding to the first solenoid actuator 401 of cutting for section 13.Particularly, solenoid actuator 401 is along the corresponding rotary timing (timing) of forward direction and camshaft 11 mobile restriction pin 601 synchronously, thereby makes

banking pin

601 and 14 engagements of the first engaging groove.Thus, slide block 21 in axial direction moves to slide block limiter 12 in response to the rotation of camshaft 11.In addition, drive banking pin 602 corresponding to the second solenoid actuator 402 of cutting for section 23.Particularly, solenoid actuator 402 synchronously moves forward banking pin 602 with the corresponding rotary timing of camshaft 11, thereby makes

banking pin

602 and 24 engagements of the second engaging groove, and the second engaging groove 24 configures in the mode that is similar to the first engaging groove 14.Thus, slide block 21 in axial direction moves to slide block limiter 22 in response to the rotation of camshaft 11.The details of aforesaid operations below will be described.

The first little lift cams 18 and first lift cams 19 are arranged on the first axial side of cutting for section 13 adjacent to each other, namely are positioned at the axial centre of slide block 21.Shown in Fig. 2 (and Fig. 4 or Fig. 6), the first little lift cams 18 and first lift cams 19 are eccentric with respect to the basic circle (imaginary circle) of a circumference on sense of rotation.In addition, first lift cams 19 with respect to the offset of basic circle greater than the offset of the first little lift cams 18 with respect to basic circle.

Placing second cuts for section 23 so that first cut to cut for left side and the right side of section 23 in Fig. 1 (and Fig. 3 or Fig. 5) for section 13 and second and be mutually symmetrical.The second little lift cams 28 and second largest lift cams 29 are arranged on the second axial side of cutting for section 23 adjacent to each other, namely are positioned at the axial centre of slide block 21.The second little lift portion 28 and second largest lift portion 29 respectively along the axial direction of camshaft 11 with respect to the first little lift cams 18 and first lift cams 19 axial dipole fields.In addition, the eccentric part of the eccentric part of the second little lift portion 28 and second largest lift portion 29 on the sense of rotation of camshaft 11 respectively from the eccentric part of the eccentric part of the first little lift cams 18 and first lift cams 19 approximately 180 degree that are shifted circumferentially.

Roller 31 and swing arm 33 be corresponding to the first little lift cams 18 and first lift cams 19, and the rotation of camshaft 11 is converted to the linear reciprocating motion of suction valve 91.In addition, roller 32 and swing arm 34 be corresponding to the second little lift cams 28 and second largest lift cams 29, and the rotation of camshaft 11 is converted to the linear reciprocating motion of suction valve 92.

Roller 31 is folded between the middle body of first little/long-nose cam 18/19 and swing arm 33.Similarly, roller 32 is folded between the middle body of second little/long-nose cam 28/29 and swing arm 34.

With reference to figure 2, an end of each

swing arm

33,34 arm contacts corresponding slack adjuster 35,36, and the other end of

swing arm

33,34 arm contacts corresponding suction valve 91,92.Corresponding clearance adjuster 35,36

swing arm

33,34 contacting part swing are touched in each

swing arm

33,34 solderless wrapped connections.When

swing arm

33,34 swung, the other end of

swing arm

33,34 arm was towards moving with

suction valve

91,92 away from correspondence.Corresponding to the clearance adjuster 35 of swing arm 33 shown in Fig. 2 (and Fig. 4 or Fig. 6).In order to simplify not shown clearance adjuster 36 corresponding to swing arm 34.

Next, the operation of valve stroke controlling device 10 will be described referring to figs. 1 to Fig. 6.

With reference to figure 1 and Fig. 2, when slide block 21 was arranged at the axial side that slide block limiter 22 is positioned at, roller 31 contacted with the outer circumferential face of the eccentric part of the first little lift cams 18, and promotes swing arm 33 downwards.And then the suction valve 91 of cylinder head 90 is opened, and, is raised lift amount (amount of the less of the lift) L1 of less that is.Roller 32 contacts with the outer circumferential face of the eccentric part of the second little lift cams 28 in corresponding phase place, and this corresponding phase place is to change approximately 180 degree from roller 31.By this way, open suction valve 92, that is, be raised lift amount L1.

In the following description, this state of valve stroke controlling device 10 is called little lift state.In addition, another state of the outer circumferential face of the eccentric part of the first lift cams 19 of roller 31 contacts is called the high-lift state.

In little lift state, the banking pin 601 of solenoid actuator 401 be arranged on the first engaging groove 14 directly over.Therefore, cutting from little lift state for when the high-lift state, solenoid actuator 401 drives banking pin 601 along forward direction, so that banking pin 601 and the first engaging groove 14 mesh in corresponding timing, rotates to the rotational position shown in Fig. 1 and 2 at this timing cam axle 11.

Under the state of

banking pin

601 and 14 engagements of the first engaging groove, when slide block 21 rotated together with camshaft 11, banking pin 601 was shifted, and meshed with front portion 15, transition part 16 and rear portion 17 successively.During this period, shown in the arrow A 1 among Fig. 1, slide block 21 moves towards slide block limiter 12 along the axial direction of camshaft 11.

In Fig. 3 and 4, the rotational position P1 of the first little lift cams 18 and first lift cams 19 is shown with solid line, and rotational position P1 is obtained from the first little lift cams 18 shown in Fig. 1 and 2 and the rotational position P0 90-degree rotation of first lift cams 19 by slide block 21.In addition, in Fig. 4, with the corresponding rotational position P2 that is shown in dotted line the first little lift cams 18 and first lift cams 19, rotational position P2 is obtained by the rotational position P0 Rotate 180 degree of slide block 21 from the first little lift cams 18 shown in Fig. 1 and 2 and first lift cams 19.In addition, in Fig. 4, with the corresponding rotational position P3 that is shown in dotted line the first little lift cams 18 and first lift cams 19, rotational position P3 is obtained by rotational position P0 rotation 270 degree of slide block 21 from the first little lift cams 18 shown in Fig. 1 and 2 and first lift cams 19.In the rotating range from position P1 to position P3, the outer circumferential face of the corresponding lift cams 18 of roller 31 contact, 19 arched part, this arched part extends archedly along basic circle.Therefore,

corresponding suction valve

91,92 remains on the valve closed condition.

In addition, the the first little lift cams 18 that after by position P3, reaches and the rotational position place of first lift cams 19, the radial groove degree of depth at rear portion 17 reduces gradually, so that the diapire at rear portion 17 promotes banking pin 601(referring to the solid arrow that makes progress among Fig. 4 along the backward directions radially outward).

Subsequently, as illustrated in Figures 5 and 6, the the first little lift cams 18 that reaches behind the P0 rotating 360 degrees of position at slide block 21 and the rotational position P4 of first lift cams 19, the outer circumferential face of the eccentric part of the first lift cams 19 of roller 31 contacts is with downward promotion swing arm 33.Particularly, valve stroke controlling device 10 is in the high-lift state now.Therefore, the suction valve 91 of cylinder head 90 is opened, and, is raised relatively large lift amount (the relatively large amount of lift) L2 that is.And then roller 32 contacts the outer circumferential face of the eccentric part of second largest lift cams 29 in corresponding phase place, and this corresponding phase place be approximately 180 to spend from the phase change of roller 31.By this way, open suction valve 92, that is, be raised lift amount L2.

Under the high-lift state, the banking pin 602 of solenoid actuator 402 be arranged on the second engaging groove 24 directly over.Therefore, cutting from the high-lift state for when the little lift state, solenoid actuator 402 drives banking pin 602 along forward direction, so that banking pin 602 and the second engaging groove 24 rotate to the rotational position shown in Fig. 5 and 6 in corresponding regularly engagement at this timing cam axle 11.

When slide block 21 when banking pin 602 rotates with camshaft 11 under the state of the second engaging groove 24 engagement, banking pin 602 is shifted, and successively with anterior 25, transition part 26 and rear portion 27 engagements.During this period, shown in the arrow A 2 among Fig. 5, slide block 21 moves towards slide block limiter 22 along the axial direction of camshaft 11.

As mentioned above, the synchronous solenoid actuator 401 of valve stroke controlling device 10 control and the rotary timing of camshaft 11,402 operation are replaced between lift amount L1 and lift amount L2

corresponding suction valve

91,92 lift amount cut.

Particularly, valve stroke controlling device 10 is come the modulating valve lift amount based on the load of engine speed and/or internal-combustion engine, suitably to improve operational condition.

Next, will be with reference to the details of Fig. 7 to 10 description as the structure of the solenoid actuator of major character of the present invention.In the following description, for the purpose of describing, two solenoid actuators 401,402 are referred to as solenoid actuator 40.Equally, solenoid actuator 401,402 banking pin 601,602 are referred to as banking pin 60.

Such as Fig. 7 and shown in Figure 10, solenoid actuator 40 comprises permanent magnet 41, coil 42, rear stator 43, front stator 44, yoke 46, holding part 47, plunger 50, banking pin 60, sleeve 70 and spring 75.These parts are installed coaxially with respect to convenience center axle O.

Plunger 50 and banking pin 60 are engaged with each other (that is, firmly being connected each other) integratedly, and with respect to other parts from the most backward position shown in Figure 7 (going-back position) to to-and-fro motion the forward facing position (most advanced) shown in Figure 10.Here, the rear stroke to the position (being also referred to as stroke amount) at plunger 50 and banking pin 60 is called as zero stroke.In addition, the stroke at the forward facing position of plunger 50 and banking pin 60 is called as full stroke.Plunger 50 and banking pin 60 on forward direction from can representing with corresponding stroke (mm) to front distance of position the most backward.In addition, in the following description, forward direction (direction of advance) and front side refer to respectively downward direction and the downside among Fig. 7 to 10, and backward direction (direction of retreat) and rear side refer to respectively upward direction and the upside among Fig. 7 to 10.

Permanent magnet 41 is static to remain on position plunger 50 and the adjacent side of close end banking pin 60 (upper end portion among Fig. 7) (that is, relative with the distal portion of banking pin 60).Permanent magnet 41 utilizes the magnetic force of permanent magnet 41 along the suction surface 511 of backward directions magnetic attraction plunger 50, so that the suction surface 511 of plunger 50 is by magnetic attraction and staticly by the magnetic attraction of permanent magnet 41 remain on the most backward position shown in Figure 7.

When coil 42 during by the energising of connector (not shown), coil 42 produces electromagnetic forces with along forward direction magnetic attraction plunger 50.

Rear stator 43 is placed on a side at permanent magnet 41 places of front stator 44 in the axial direction.Stator 43 and front stator 44 are made by magnetic substance after each.In addition, the appropriate section of the interior perimembranous of the corresponding axial end portion of stator 43 and front stator 44 covering coils 42 and coil 42 after each.Particularly, as shown in Figure 8, rear stator 43 comprises rear wall 431 and inwall 432.Rear wall 431 covers the rearward end of coil 42, and inwall 432 covers the rear portion of the interior perimembranous of coil 42.Front stator 44 comprises antetheca 441 and inwall 442.Antetheca 441 covers the front end of coil 42, and inwall 442 covers the front portion of the interior perimembranous of coil 42.The opening surface 443 of the opening surface 433 of the inwall 432 of rear stator 43 and the inwall 442 of front stator 44 is along banking pin 60(and plunger 50) axial direction (namely, the axial direction of central shaft O) axially relatively, so that form in the axial direction gap 45 between opening surface 433 and the opening surface 443.

The slidably section 52 of plunger 50 is configured to slide along the inwall 442 of the inwall 432 of rear stator 43 and front stator 44.In addition, rear stator 43 and front stator 44 form the stream (being also referred to as conducting path or magnetic circuit) of magnetic flux ф, and magnetic flux ф is produced when it is switched on by coil 42.At this moment, because the existence in gap 45, magnetic flux ф passes plunger 50 and flows to front stator 44 from rear stator 43.

Yoke 46 is made by magnetic material, and is configured to tubular to cover the peripheral part of coil 42.Stator 43 and front stator 44 were to form the stream (conducting path) of magnetic flux ф after yoke 46 cooperated, and magnetic flux ф is produced when it is switched on by coil 42.

Holding part 47 joins (that is, firmly being connected to) yoke 46 after-openings 461 to.Holding part 47 is configured to cup-shaped (having perisporium and diapire) to hold permanent magnet 41.Holding part 47 is made by magnetic material and is formed opening in the axial side relative with the suction surface 511 of plunger 50.

Particularly, as shown in Figure 9, the opening side end face 471 of the opening that is adjacent to holding part 47 (opening end) of holding part 47 is outstanding towards plunger 50 from the end face 411 of permanent magnet 41.Particularly, the suction surface 511 of the flange 51 that is formed on plunger 50 keeps static state by magnetic attraction and by the magnetic attraction of permanent magnet 41 under, the opening side end face 471 of suction surface 511 contact holding parts 47.At this moment, gap delta is formed between the suction surface 511 of flange 51 of the end face 411 of permanent magnet 41 and plunger 50.In the present embodiment, the external diameter of permanent magnet 41 is greater than the external diameter of the slidably section 52 of plunger 50, but less than the external diameter of flange 51.

Plunger 50 is made by magnetic material, and comprises flange 51 and section 52 slidably.Flange 51 is formed on the rearward end of plunger 50 and has larger diameter.Slidably section 52 extends axially the front end of plunger 50 from flange 51.

The suction surface 511 that is located axially at the flange 51 of permanent magnet 41 sides always receives the magnetic attraction of permanent magnet 41.Slidably the outer wall 521 of section 52 is configured to slide along the inwall 432 of rear stator 43 and the inwall 442 of front stator 44.The joint 61 of banking pin 60 is accommodated in the attachment hole 522 of section 52 slidably, thereby plunger 50 and banking pin 60 are engaged integratedly, that is, connect securely each other.The seating plane 621 of the spring fitting section 62 of banking pin 60 and distal face 523 adjacency of part 52 slidably.

Referring again to Fig. 8, is under the working state of zero stroke at the stroke of plunger 50, and the axial position of the opening surface 443 of front stator 44 is set to basically consistent with the axial position of the distal face 523 of section 52 slidably.Here, basically identical opening surface 443 and the distal face 523 of referring to of the axial position of the axial position of opening surface 443 and distal face 523 is axially disposed within the state in the corresponding axial range, measures this axial range at the axial direction of central shaft O.This corresponding axial range can change to several millimeters from hundreds of microns, and as understanding under the instruction of the general knowledge in the solenoid actuator technical field, for example can realize by forming chamfering on one or more edges of opening surface 443 and/or distal face 523.

As mentioned above, when in the situation that plunger 50 when to be the axial position of axial position and opening surface 443 of zero stroke distal face 523 basically consistent each other, minimizes the magnetic gap Gm between plunger shown in Figure 8 50 and the front stator 44.Thus, be in the moment that the coil 42 under the non-power status begins to switch on, flow to front stator 44 from plunger 50 by minimized magnetic gap Gm most effectively by the magnetic flux ф of coil 42 instantaneous generations.In addition, the density of magnetic flux ф increases owing to the section area in the path of magnetic flux ф gets clogged at clearance G m place.As a result, under the state shown in Figure 8, can obtain maximum electromagnetic force.

When plunger 50 when being illustrated by the broken lines forward direction among Fig. 8 and moving, plunger 50 and front stator 44 overlap each other in the axial direction, thereby the cross section in the path of magnetic flux ф is increased.Therefore, the density of magnetic flux ф reduces.As a result, the electromagnetic force of coil 42 reduces.

Banking pin 60 has joint 61, spring fitting section 62, slidably section 63 and distal portion 64, and it is coaxially placed along central shaft O, and arranges one by one from near-end (upper end Fig. 7) beginning of banking pin 60 with this order.Joint 61 is connected to plunger 50.Spring 75 is installed in the outer peripheral portion of spring fitting part 62.

Slidably the outer wall of section 63 can slide along the inwall of the sliding eye 721 of sleeve 70.Slidably form the seat surface 631 of the front end (underpart among Fig. 7) of support spring 75 on the ladder surface between section 63 and the spring fitting section 62.

The outer wall 641 of distal portion 64 is accommodated in the receiving bore 722 of sleeve 70.When banking pin 60 is placed on the most backward position shown in Fig. 7, the distal face of distal portion 64 (lower end surface among Fig. 7) 643 is basically coplanar with end face (lower end surface among Fig. 7) 723 of sleeve 70, or departs from a little at axial inboard end face 723 with sleeve 70.In addition, when banking pin 60 moved forward along forward direction, distal face 643 was outstanding from the end face 723 of sleeve 70, and with corresponding engaging

groove

14,24 engagements of valve stroke controlling device 10.

Sleeve 70 comprises flange 71 and main part 72.

The periphery wall of flange 71 joins the under shed among open front 462(Fig. 7 of (namely securely being connected to) yoke 46 to).In addition, the antetheca 441 of the peripheral edge of the ear end face of flange 71 contact front stator 44.And in sleeve 70, the recess 711 that holds spring retaining plate 76 is formed on the radially inner side of peripheral edge of ear end face of flange 71.

Main part 72 has sliding eye 721 and receiving bore 722, and it is coaxial each other along central axis O.Sliding eye 721 holds the slidably section 63 of banking pin 60.Receiving bore 722 holds the distal portion 64 of banking pin 60.

Spring 75 is installed on the outer peripheral portion of spring fitting section 62.Spring 75 has two ends, and it is supported by spring retaining plate 76 and the seat surface 631 of banking pin 60 respectively.Spring 75 applies elastic force (thrust) to promote banking pin 60 and plunger 50 in forward direction.

Spring retaining plate 76 is contained in the recess 711 of flange 71 of sleeve 70 and the rearward end of support spring 75.

Next, with reference to Figure 11 and 12 the in the above described manner operation of the solenoid actuator 40 of structure is described.

As shown in Figure 11, under coil 42 non-power status, be applied to plunger 50 by the magnetic attraction Fm of permanent magnet 41 generations and the elastic force Fsp that is produced by spring 75.

Apply magnetic attraction Fm along backward directions (mobile plunger 50 is away from the direction of camshaft 11 backward).Magnetic attraction Fm is maximum when zero stroke (that is, the 0mm stroke of plunger 50).When the stroke of plunger 50 increased, magnetic attraction Fm reduced.It should be noted that according to Coulomb's law square the reducing inversely of magnetic attraction Fm and stroke.Apply magnetic attraction Fm along backward directions (mobile plunger 50 is away from the direction of camshaft 11 backward).Magnetic attraction Fm is maximum when zero stroke (that is, the 0mm stroke of plunger 50).When the stroke of plunger 50 increased, magnetic attraction Fm reduced.When the 0mm of plunger 50 stroke, magnetic attraction Fm is set to greater than elastic force Fsp.Therefore, plunger 50 is by magnetic attraction, and the magnetic attraction by permanent magnet 41 keeps being still in rear to the position under the non-power status of coil 42.

By this way, the distal portion 64 of banking pin 60 is contained in the radially inside position of end face 723 of sleeve 70.Thus, in valve stroke controlling device 10, banking pin 60 and corresponding engaging

groove

14,24 engagement are released, that is, banking pin 60 breaks away from corresponding engaging

grooves

14,24.

As shown in Figure 12, when coil 42 energising, except magnetic attraction Fm and elastic force Fs, also apply along the electromagnetic force Fsol of forward direction magnetic attraction plunger 50 to plunger 50.

As mentioned above, at the zero stroke position place of plunger 50, the axial position of the axial position of the opening surface 443 of front stator 44 and the distal face 523 of plunger 50 is basically consistent with each other.Thereby, in the moment the coil 42 of the non-power status that is in coil 42 begins to switch on, can obtain maximum magnetic force Fsol.Particularly, magnetic attraction Fsol is maximum when the 0mm stroke, and reduces along with the increase of stroke.

In addition, within comprising the whole stroke range of 0 millimeter stroke, with electromagnetic force Fsol and elastic force Fsp make a concerted effort set for greater than magnetic attraction Fm.By this setting, plunger 50 can discharge from the magnetic attachment of permanent magnet 41, and can move to full stroke Sf along forward direction.Here, even should be noted that as electromagnetic force Fsol at plunger 50 along vanishing in the moving process of forward direction or approach zero, also can be separately by elastic force Fsp mobile plunger 50 on forward direction.

By this way, the distal portion 64 of banking pin 60 from the end face 723 of sleeve 70 outstanding and with corresponding engaging

groove

14,24 engagements of valve stroke controlling device 10.Slide block 21 moves axially to the precalculated position by the rotation of camshaft 11, to change valve-lift amount.

By corresponding when cutting for the axial motion of

section

13,23 rotation and slide block 21 that radially outward promotes the distal portion 64 of banking pin 60 on backward directions, plunger 50 moves to the one-stroke scope from full stroke Sf on backward directions, this stroke range is equal to or less than the stroke threshold value St on backward directions.

In the stroke range that is equal to or less than stroke threshold value St, magnetic attraction Fm becomes and is higher than elastic force Fsp.Therefore, plunger 50 is attracted permanent magnet 41 along backward directions, until the opening side end face 471 of the suction surface 511 contact holding parts 47 of plunger 50.At this moment, gap delta is formed between the suction surface 511 of the end face 411 of permanent magnet 41 and plunger 50, thereby makes plunger 50 can not bump against permanent magnet 41.

The advantage of the solenoid actuator 40 of the present embodiment will be described now.

(1) in the solenoid actuator 40 of the present embodiment, permanent magnet 41 keeps static.Therefore, compare with the solenoid actuator of the driving permanent magnet of prior art, can limit the fracture (or breaking) of the permanent magnet that the vibrations when driving permanent magnet cause, thereby can be in off working state by limiting actuator.

(2) made by the magnetic material for the holding part 47 of holding permanent magnet 41.Therefore, the magnetic flux bleed-through of permanent magnet 41 can be limited, and the magnetic attraction Fm of permanent magnet 41 can be improved.In addition, even in the situation that permanent magnet 41 fractures can also limit the dispersion of the fracture fragment of permanent magnet 41.

(3) opening side end face 471 of holding part 47 is outstanding towards plunger 50 from the end face 411 of permanent magnet 41, and gap delta is formed between the suction surface 511 of the end face 411 of permanent magnet 41 and plunger 50.Therefore, when plunger 50 attracted to permanent magnet 41, the suction surface 511 of plunger 50 contacted the opening side end face 471 of holding parts 47, and can not bump against the end face 411 of permanent magnet 41.Like this, can limit the fracture of permanent magnet 41.

In addition, plunger 50 does not directly contact permanent magnet 41, thus in time deteriorated of the magnetic property that can limit permanent magnet 41.

(4) axial position 433 of the opening surface 433 of front stator 44 keeps being still in rear basically consistent with the axial position of the distal face 523 of plunger 50 under the state of position by magnetic attraction and by the magnetic attraction of permanent magnet 41 at plunger 50.Therefore since when plunger 50 moves along forward direction overlapping between plunger 50 and the front stator 44, the density of magnetic flux reduces, and the electromagnetic force Fsol of coil 42 reduces.By this way, it is maximum that electromagnetic force Fsol reaches at 0mm stroke place, and when the 0mm stroke, needs are resisted the magnetic attraction Fm of permanent magnet 41 when the operation of beginning valve stroke controlling device 10 and plunger 50 is moved away from permanent magnet 41.Thereby, can effectively produce electromagnetic force Fsol.Therefore, can reduce the size of coil 42.

(5) in the solenoid actuator 40 of the present embodiment that is applied to valve stroke controlling device 10, when the distal portion 64 that makes banking pin 60 moves away from corresponding engaging

groove

14,24, by torque radially outward promotion banking pin 60 on backward directions of camshaft 11.Therefore, needn't provide special-purpose drive unit (driver module) to drive banking pin 60 with the forward facing position from banking pin 60 along backward directions.Therefore, compare with the solenoid actuator of the JPH07-335434A that comprises two solenoid driving devices that are separately positioned on forward direction side and backward directions side, can reduce the size of solenoid actuator.

The present invention is not limited to above-described embodiment, can make amendment to above-described embodiment under the principle of present disclosure.For example, above-described embodiment can be amended as follows.

(a) material that holds the holding part 47 of permanent magnet 41 is not limited to magnetic material.For example, the holding part 47 of holding permanent magnet 41 can be made by nonmagnetic metal material (for example, Austenitic Stainless Steel) or resin material.

(b) opening side end face 471 of holding part 47 is not necessarily outstanding towards plunger 50 from the end face 411 of permanent magnet 41.For example, the opening side end face 471 of holding part 47 is can be basically coplanar or can be axially recessed from the end face 411 of permanent magnet 41 with the end face 411 of permanent magnet 41.

The axial position of the distal face 523 of the plunger 50 when (c) axial position of the opening surface 443 of front stator 44 can be with the zero stroke of plunger 50 is consistent.

(d) the valve stroke controlling device of present disclosure can be the valve stroke controlling device of regulating the lift amount of respective row air valve.

(e) for example the

cam

18,19,28 of valve

stroke controlling device

10,29 and the structure of slide block 21 be not limited to above-described embodiment, and as long as moving to cut and replacing of the banking pin that cam and slide block can be by corresponding solenoid actuators just can be made amendment to said structure by rights.

As mentioned above, present disclosure is not limited to above-described embodiment and modification thereof.That is, above-described embodiment and modification thereof can also be made amendment in every way, and do not deviate from the principle of present disclosure.

Claims

1. solenoid actuator that is used for valve stroke controlling device (10), described valve stroke controlling device (10) are regulated the lift amount of one of the suction valve (91,92) of internal-combustion engine and outlet valve, and described solenoid actuator comprises:

Banking pin (60,601,602), its be configured to towards with engaging groove (14 away from slide block (21), 24) to-and-fro motion, described slide block (21) can rotate integratedly with the camshaft (11) of described valve stroke controlling device (10) and can move with respect to described camshaft (11) along the axial direction of described camshaft (11), wherein:

When described banking pin (60,601,602) along the described engaging groove (14 of forward direction towards described slide block (21), when 24) moving, described banking pin (60,601,602) distal portion (64) can mesh with the described engaging groove (14,24) of described slide block (21);

When described banking pin (60,601,602) utilize the backward directions opposite with described forward direction from the torque edge that described camshaft (11) applies away from the engaging groove (14 of described slide block (21), when 24) moving, described banking pin (60,601,602) described distal portion (64) breaks away from the described engaging groove (14,24) of described slide block (21);

Plunger (50), it is made by magnetic material and has an end that is fastenedly connected with described banking pin (60,601,602);

Permanent magnet (41), it is static to remain on corresponding position, corresponding position is positioned at described plunger (50) and described banking pin (60,601,602) the relative side of described distal portion (64), wherein said permanent magnet (41) apply magnetic attraction magnetically to attract the suction surface (511) of described plunger (50) on described backward directions;

Coil (42), to after described coil (42) energising, described coil (42) produces electromagnetic force, magnetically attracting described plunger (50) on described forward direction, thereby moves described plunger (50) along described forward direction; And

Spring (75), it promotes described banking pin (60,601,602) and described plunger (50) along described forward direction.

2. solenoid actuator according to claim 1, also comprise holding part (47), it is made by magnetic material, wherein, described holding part (47) forms opening in a side at described suction surface (511) place of described plunger (50), and described holding part (47) is held described permanent magnet (41).

3. solenoid actuator according to claim 2, wherein, the opening side end face (471) of described holding part (47) is outstanding towards described plunger (50) from the end face (411) of described permanent magnet (41).

4. each described solenoid actuator in 3 according to claim 1 also comprises rear stator (43) and front stator (44), and described rear stator (43) and described front stator (44) are made by magnetic material, wherein:

Described rear stator (43) and described front stator (44) are being positioned between described coil (42) and the described plunger (50) in the radial direction, and be located axially at described permanent magnet (41) and described banking pin (60,601,602) between the described distal portion (64);

Described rear stator (43) is placed on a side at described permanent magnet (41) place of described front stator (44) at described axial direction;

Gap (45) is interposed between described rear stator (43) and the described front stator (44) at described axial direction;

Described rear stator (43) and described front stator (44) are configured to by described plunger (50) conduction magnetic flux therebetween; And

When described plunger (50) kept static by magnetic attraction and by the described magnetic attraction of described permanent magnet (41), the axial position of the opening surface that is exposed to described gap (45) (433) of described front stator (44) was basically consistent with the axial position of the distal face (523) of described plunger (50).

5. each described solenoid actuator in 3 according to claim 1, also comprise at least one stator (43,44), it is located axially between described coil (42) and the described plunger (50), wherein, the external diameter of described permanent magnet (41) can be along the external diameter of the slidably section (52) that described at least one stator (43,44) slides greater than described plunger (50).