CN101594972B - Mold clamping device for injection molding machine - Google Patents
Mold clamping device for injection molding machine Download PDFInfo
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- CN101594972B CN101594972B CN200880001388XA CN200880001388A CN101594972B CN 101594972 B CN101594972 B CN 101594972B CN 200880001388X A CN200880001388X A CN 200880001388XA CN 200880001388 A CN200880001388 A CN 200880001388A CN 101594972 B CN101594972 B CN 101594972B
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- matched moulds
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- bearing
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B29—WORKING OF PLASTICS; WORKING OF SUBSTANCES IN A PLASTIC STATE IN GENERAL
- B29C—SHAPING OR JOINING OF PLASTICS; SHAPING OF MATERIAL IN A PLASTIC STATE, NOT OTHERWISE PROVIDED FOR; AFTER-TREATMENT OF THE SHAPED PRODUCTS, e.g. REPAIRING
- B29C33/00—Moulds or cores; Details thereof or accessories therefor
- B29C33/20—Opening, closing or clamping
- B29C33/22—Opening, closing or clamping by rectilinear movement
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B22—CASTING; POWDER METALLURGY
- B22D—CASTING OF METALS; CASTING OF OTHER SUBSTANCES BY THE SAME PROCESSES OR DEVICES
- B22D17/00—Pressure die casting or injection die casting, i.e. casting in which the metal is forced into a mould under high pressure
- B22D17/20—Accessories: Details
- B22D17/26—Mechanisms or devices for locking or opening dies
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B29—WORKING OF PLASTICS; WORKING OF SUBSTANCES IN A PLASTIC STATE IN GENERAL
- B29C—SHAPING OR JOINING OF PLASTICS; SHAPING OF MATERIAL IN A PLASTIC STATE, NOT OTHERWISE PROVIDED FOR; AFTER-TREATMENT OF THE SHAPED PRODUCTS, e.g. REPAIRING
- B29C45/00—Injection moulding, i.e. forcing the required volume of moulding material through a nozzle into a closed mould; Apparatus therefor
- B29C45/17—Component parts, details or accessories; Auxiliary operations
- B29C45/64—Mould opening, closing or clamping devices
- B29C45/68—Mould opening, closing or clamping devices hydro-mechanical
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B29—WORKING OF PLASTICS; WORKING OF SUBSTANCES IN A PLASTIC STATE IN GENERAL
- B29C—SHAPING OR JOINING OF PLASTICS; SHAPING OF MATERIAL IN A PLASTIC STATE, NOT OTHERWISE PROVIDED FOR; AFTER-TREATMENT OF THE SHAPED PRODUCTS, e.g. REPAIRING
- B29C45/00—Injection moulding, i.e. forcing the required volume of moulding material through a nozzle into a closed mould; Apparatus therefor
- B29C45/17—Component parts, details or accessories; Auxiliary operations
- B29C2045/1784—Component parts, details or accessories not otherwise provided for; Auxiliary operations not otherwise provided for
- B29C2045/1792—Machine parts driven by an electric motor, e.g. electric servomotor
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Manufacturing & Machinery (AREA)
- Moulds For Moulding Plastics Or The Like (AREA)
- Injection Moulding Of Plastics Or The Like (AREA)
Abstract
A mold clamping device is provided for performing mold opening/closing by rotating a ball screw (60) fixed movably to a back platen (20) through a servo motor (40) and performing mold clamping by applying a mold clamping force to a flange-like member (62) integrated with the ball screw by a mold claming ram (50). A movable platen (30) has an operating shaft (31), with a ball nut (61) and a sliding bearing (32) at the distal end of the operation shaft. The flange-like member is arranged at a position against which the mold claming ram abuts only when it advances at the time of mold clamping. The mold claming ram is pressed in the mold opening direction by a push-in means (53). The mold clamping device slides the distal end of the operating shaft of the movable platen in its back platen under a state where the mold claming ram is spaced apart by a predetermined clearance L from the flange-like member when the mold is opened/closed, and presses the flange-like member by the mold claming ram.
Description
Technical field
The present invention relates to by servo motor by the electronic mold closing mechanism that carries out the mould switching, carried out the injection (mo(u)lding) machine of matched moulds by the matched moulds pressure head by hydraulic pressure.
Background technology
By the electronic hybrid mold closing mechanism that carries out the mould switching, carries out matched moulds by hydraulic pressure, the mold clamping force by brute force in precision control mould on-off action carries out mould assembling action.In this hybrid mold closing mechanism, the type of directly bearing the type of mold clamping force and not bearing mold clamping force is arranged on ball-screw.
The present invention relates to be the former directly bear the mold closing mechanism of mold clamping force at ball-screw.In this mold closing mechanism, the type that is proposed by (Japan) JP 7-71807 communique (patent documentation 1) is for example arranged.This mold closing mechanism is fixed on the movable plate side with ball screw (being equivalent to ball-screw), and the ball nut that is threadedly engaged with it is bearing on the end plate (being equivalent to reverse platen) by axle.
In more detail, this mold closing mechanism has: fix the moving retainer of the simultaneously relative end plate movable revolvable of this ball nut, produced the matched moulds pressure head of mold clamping force during matched moulds by hydraulic pressure, be formed at the friction clutch section of this matched moulds pressure head; Described matched moulds pressure head is left from described retainer, when matched moulds, make in addition their butts.Therefore, this mold closing mechanism puts on described ball screw to mold clamping force from this friction clutch via retainer when matched moulds, matched moulds is carried out in the rotation that prevention produces between described ball screw and ball nut simultaneously, in addition, when die sinking, the suitable force feed of adding is carried out die opening and closing under the state that this matched moulds pressure head and retainer are left in two grease chambeies of the A of pumping chamber and the C of pumping chamber.
According to this mold closing mechanism, because the rotating torque that produces between ball screw and ball nut when matched moulds is stoped by the braking moment that forms by friction clutch, so the mold clamping force that bears between this ball screw and ball nut is restricted to static load.Therefore, ball screw is compared Miniaturizable, path with ball nut with the occasion of bearing dynamic load, and its life-span is also elongated.
Patent documentation 1:(Japan) JP 7-71807 communique
In addition, recently, along with the metal die high precision int, the core of metal die and die cavity chimeric, perhaps guide finger, with the chimeric progressively high precision int of angle pin and this pilot hole.In addition, the positive miniaturization of the transfer surface of formed products.Therefore, day by day require consumingly the high precision int of grazing of the die opening and closing action of mold closing mechanism.
, the not special intention that improves the grazing of this die opening and closing action of above-mentioned mold closing mechanism.This be because, the first, elongated ball screw is two supports, drive to rotate by Timing Belt between these supporting-points, is subject to the cause with the power of axial quadrature.The second, be because the ball nut axle is bearing on the retainer, the cause of the formation of the complexity of being combined with belt wheel by connecting member simultaneously.In addition, the 3rd, be because the formation cause that ball nut is rotated.
In first consists of, there is not the ball screw of abundant rigidity at bending direction, owing to apply the power (normal load) of above-mentioned quadrature in the centre position in the interval of two supports, so on ball screw, easily produce crooked.Therefore, produce the deflection that formed by its normal load, be rotational vibrations at ball screw, it directly affects the movable plate side and easily damages the grazing of this mould on-off action.Certainly, the formation itself at the above-mentioned normal load of ball screw burden that is in compressive state is the formation that originally just should avoid as far as possible.
In addition, in second consists of, because the rotatory force that is driven by Timing Belt is via a plurality of parts transmission of belt wheel, connecting member, ball nut and retainer, so the rigidity of these parts or machining accuracy (for example concentricity) accumulation, unimaginable rotational vibrations easily occurs in the result.
In addition, in the 3rd consisted of, the lubricated inadequate possibility of ball nut side was large.Generally be owing to self causing lubricating oil to spill and undesirable cause in the rotation of ball nut side.
Summary of the invention
Therefore, even the object of the present invention is to provide the mold closing mechanism that has also solved the problems referred to above at the hybrid mold closing mechanism of ball-screw effect mold clamping force.
The mold closing mechanism of injection (mo(u)lding) machine of the present invention in order to solve above-mentioned problem, is constructed as follows.
The mold closing mechanism of the injection (mo(u)lding) machine of the first technical scheme of the present invention has fixed platen, oppositely platen reaches movable platen mobile between them, using the feed screw mechanism that is rotated by servo motor driven to carry out mould opens and closes, carry out the injection (mo(u)lding) machine of matched moulds with the hydraulic means that comprises the matched moulds pressure head, in this mold closing mechanism;
Described servo motor and described matched moulds pressure head are located at described reverse platen side, the ball nut that described feed screw mechanism is bearing in the ball-screw of described reverse platen side by axle and is fixed on described movable platen side consists of, this ball-screw is combined with described servo motor by means of rotation transfer mechanism on the position of the die sinking direction side of this axle bearing position, described movable platen has to the side-prominent action axle of described reverse platen, front end at this action axle is installed with described ball nut and sliding bearing, has simultaneously the hollow hole that allows described ball-screw to enter at this center, described reverse platen has the porose ledge of the pilot hole that forms the described sliding bearing of sliding bearing, make the cylinder body body of the matched moulds cylinder body of described matched moulds pressure head advance and retreat with formation, in this matched moulds cylinder body, the spline parts stop the rotation of described matched moulds pressure head, in addition, pressing mechanism is used more than or equal to the pressing-in force of die opening and closing power and is pressed this matched moulds pressure head and make it to retreat, the position of the described matched moulds pressure head butt that advances with matched moulds time of described ball-screw has blade of a sword shape parts in addition, and built-in axle supports the support of described ball-screw and accommodated movably in the limiting part of the rear end of being fixed in described cylinder body body with the bearing cage spare of bearing;
When die opening and closing, to the described pressing-in force of described matched moulds pressure head described bearing cage spare is pressed by described pressing mechanism by this matched moulds pressure head, retreat into this Limitation Of Movement position, described blade of a sword shape parts remain on the position of leaving this matched moulds pressure head specified gap, in addition, when matched moulds, described matched moulds pressure head is resisted described pressing-in force and is advanced, press described blade of a sword shape parts, simultaneously, leave described bearing cage spare, this bearing cage spare discharges load among described limiting part, allow simultaneously retreating of this reverse platen and matched moulds amount certain degree.
The mold closing mechanism of the injection (mo(u)lding) machine of the present invention's the second technical scheme, in the mold closing mechanism of above-mentioned the first technical scheme, when the reverse efficiency that the bearing surface coefficient of friction at the bearing surface of establishing described blade of a sword shape parts and described matched moulds pressure head is μ, establish described ball-screw was η, the helical pitch P that can make this matched moulds pressure head and the effective diameter D of the bearing surface of these blade of a sword shape parts form relative this ball-screw surpassed roughly (η/μ π) external diameter doubly.
The mold closing mechanism of the injection (mo(u)lding) machine of the present invention's the 3rd technical scheme, in the mold closing mechanism of above-mentioned the second technical scheme, described matched moulds cylinder body is made of the single action cylinder body that only has matched moulds side grease chamber, and described pressing mechanism also can be by pressing described matched moulds pressure head and the Compress Spring that makes it to retreat consists of by described pressing-in force to the die sinking direction.
The mold closing mechanism of the injection (mo(u)lding) machine of the present invention's the 4th technical scheme, in the mold closing mechanism of above-mentioned the second technical scheme, described matched moulds cylinder body is made of the bi-directional drive cylinder body with matched moulds side grease chamber and these two grease chambeies, matched moulds opposition side grease chamber, and described pressing mechanism is by by supplying with force feed, utilizing described pressing-in force to press described matched moulds pressure head and the hydraulic means that makes it to retreat consists of in the die sinking direction to this matched moulds opposition side grease chamber.
The mold closing mechanism of the injection (mo(u)lding) machine of the present invention's the 5th technical scheme, the above-mentioned the 3rd or the mold closing mechanism of the 4th technical scheme in, also comprise the safety device that allows described ball-screw to retreat when unusual, this safety device comprises the damper piston of any slip in relative these parts between described bearing cage spare and described limiting part;
In the periphery of this damper piston and the interior week of this limiting part, produce the part with the level in gap when forming mutually combination, simultaneously, the mutual gap of this part with the level consists of the extrusion grease chamber that supplies with hydraulic operation oil, supply with hydraulic operation oil by extrude the grease chamber to this, this damper piston is forwards extruded usually the time, and when unusual, be allowed to retreat, in addition, also can in the interior week of this damper piston and the periphery of this bearing cage spare, limit the abutment portion with the level that retreats limit positions of this bearing cage spare when forming mutually combination.
The mold closing mechanism of the injection (mo(u)lding) machine of the present invention's the 6th technical scheme, the above-mentioned the 3rd or the mold closing mechanism of the 4th technical scheme in, described feed screw mechanism also can be made of the screw mechanism that comprises trapezoidal screw or square leading screw.
According to the mold closing mechanism of the first technical scheme of the present invention and since the action axle of movable platen in the pilot hole of reverse platen often by the sliding supported condition guiding, so the grazing of die opening and closing action becomes high accuracy.In addition, this movable platen is supported by two positions leaving of pull bar and sliding bearing, so this grazing does not change in mold closing position and die sinking position.And porose ledge and action axle with pilot hole all are high rigid elements, so can guarantee the grazing that rigidity is high.In addition, rotation transfer mechanism is positioned at from the axle supporting on the position that die sinking direction side is left, so the ball-screw part of bearing compression load is not acted on fully the power of quadrature.In addition because this rotation transfer mechanism is the simple formation that belt wheel only is set, so rigidity defective that fully can production part or concentricity bad etc. on ball-screw unimaginable large rotational vibrations.In addition, be fixed on the action axle that ball nut do not rotate, so also can be to the lubricated obstacle that produces because consist of.In addition, matched moulds pressure head and blade of a sword shape parts leave the action of specified gap when die opening and closing, owing to only being undertaken by the pressing of pressing mechanism as spring, so be used for the formation of these departure motions and control simple and the increase reliability.In addition, when matched moulds, because leaving the matched moulds pressure head, bearing cage spare discharges load, so do not bear mold clamping force in the support of ball-screw fully with bearing.In addition, owing to when die opening and closing, only bearing die opening and closing power at bearing cage spare, so to bear the die opening and closing power especially less than mold clamping force with bearing 55 just passable as long as support.
Mold closing mechanism according to a second technical aspect of the present invention, because it is larger than requirement ratio to consist of the helical pitch P of the relative ball-screw of effective diameter D of blade of a sword shape parts, so the braking moment that produces between matched moulds pressure head and the blade of a sword shape parts when matched moulds can be conscientiously greater than the rotating torque that is produced by ball-screw.Therefore, the load that acts between ball-screw and the ball nut becomes stable static load.
Mold closing mechanism according to a third technical aspect of the present invention, because mold closing mechanism constitutes the single action cylinder body, described pressing mechanism constitutes Compress Spring, so the simultaneously hydraulic control of the simple structure of this pressing mechanism is simple.
Mold closing mechanism according to a fourth technical aspect of the present invention, mold closing mechanism constitutes the bi-directional drive cylinder body, described pressing mechanism consists of as this matched moulds opposition side grease chamber, so the departure motion of matched moulds pressure head and blade of a sword shape parts is not the passive action that is formed by spring force but by the positive action that hydraulic pressure forms, can conscientiously controls.In addition, can obtain certain pressing-in force with stroke is irrelevant.
Mold closing mechanism according to the 5th technical scheme of the present invention, when common die opening and closing, relatively be positioned at the damper piston of the limit positions of advancing, bearing cage spare is positioned at and retreats limit positions, support remains on it with the relative limiting part of bearing and retreats limit positions, in addition, allows when unusual, bearing cage spare retreats with the relative limiting part of damper piston, supports to retreat with the relative limiting part of bearing.Therefore, when unusual, produce the moment permission threaded integral that impacts in the threaded portion of ball-screw and retreat, can append the function of this impact of buffering.
According to the mold closing mechanism of the 6th technical scheme of the present invention, so increase the area that bears load because the flank of feed screw mechanism becomes ladder plane, improve withstand load.In addition, the lubricant effect in the time of can maintaining dynamic die opening and closing between leading screw and the nut, in addition, the friction that increases between it in the time of also can be to the matched moulds of static state brings action effect.Therefore, because the moment that in this feed screw mechanism, rotates hardly, so the effective diameter of blade of a sword shape parts is diminished.
Description of drawings
Fig. 1 is the cutaway view of the integral body of expression mold closing mechanism of the present invention.
Fig. 2 is the cutaway view of the major part of expression mold closing mechanism of the present invention.
Fig. 3 is the mould open and-shut mode of expression mold closing mechanism of the present invention and the cutaway view of matched moulds state, and the cutaway view of center line upside represents the mould open and-shut mode, and the cutaway view of downside represents the matched moulds state.
Fig. 4 is the cutaway view of major part of the mold closing mechanism of expression another embodiment of the present invention.
Fig. 5 is the cutaway view of major part of the mold closing mechanism of expression another embodiment of the invention.
Description of reference numerals
1 mold closing mechanism; 10 fixed platen; 20 reverse platens; The 20a pilot hole; The porose ledge of 20b; 30 movable platens; 31 action axles; The 31a hollow hole; 32 sliding bearings; 40 servo motors; 50 matched moulds pressure heads; 51 matched moulds cylinder bodies (cylinder body body); 51a matched moulds side grease chamber; 51b matched moulds opposition side grease chamber; 52 spline parts; 53 pressing mechanisms (Compress Spring); 54 limiting parts; 55 support bearings; 58 bearing cage spares; 59 damper pistons; The 59a grease chamber; 59b abutment portion with the level; 60 ball-screws; 61 ball nuts; 62 blade of a sword shape parts; 70 rotation transfer mechanisms.
The specific embodiment
The summary situation of mold closing mechanism is described at first.As shown in Figure 1, mold closing mechanism 1 has fixed platen 10, the reverse platen 20 that fixation side metal die 2a is installed, the movable platen 30 that remains on the state ground movement that movable metal die 2b is installed therebetween; This fixed platen and reverse platen are fastening by pull bar 3.In addition, this movable platen carries out die opening and closing by the electric device of servo motor 40 grades, carries out matched moulds by the hydraulic means with matched moulds pressure head 50.The elongation of the pull bar 3 that is formed by mold clamping force as the matched moulds amount is as described in rear, is presented as that reverse platen 20 is to the displacement of die sinking direction (following be rear).
The formation of the present invention for adopting in so hybrid mold closing mechanism describes its major part together with Fig. 2.
In mold closing mechanism 1 of the present invention, servo motor 40 is fixed on reverse platen 20.In addition, make the matched moulds cylinder body of matched moulds pressure head 50 advance and retreat as the end parts of the rear side of the reverse platen 20 of cylinder body body 51 formations.In addition, matched moulds pressure head 50 stops rotation by spline parts 52 among this cylinder body body, rearward pressed with the pressing-in force more than the die opening and closing power by pressing mechanism 53 simultaneously.
Feed screw mechanism is by being consisted of by the axle ball-screw 60 that supports and the ball nut 61 that is fixed on described movable platen side in reverse platen side.In addition, this ball-screw is combined with this servo motor by rotation transfer mechanism 70 described later in the rear position of the position of being supported by this axle, and in addition, the position of the matched moulds pressure head 50 that butt advances when matched moulds has blade of a sword shape parts 62.
Oppositely platen 20 comprises porose ledge 20b at its rear side, and this porose ledge 20b has the pilot hole 20a of the sliding bearing 32 of sliding bearing action axle 31 front ends.In addition, oppositely platen 20 has the cylinder body body 51 that forms above-mentioned matched moulds cylinder body in the rear end of this porose ledge 20b, has the limiting part 54 for the prolongation 60a of removable earth's axis rotating bearing ball leading screw 60 in the rear end of this cylinder body body.
The more specifically embodiment of mold closing mechanism 1 of the present invention consists of as described below.
The rotation transfer mechanism 70 of ball-screw 60 is by the belt wheel 72 of the belt wheel 71 of servo motor side and ball-screw side and opens betwixt existing known that the Timing Belt 73 established consists of and consist of.
Ball-screw 60 have the rear that extends to threaded portion prolongation 60a and as with the stage portion that meets the boundary of this threaded portion.In addition, in the threaded portion side of this prolongation 60a, with the state of this stage portion butt under fixing blade of a sword shape parts 62.Therefore, the mold clamping force that by matched moulds pressure head 50 these blade of a sword shape parts is born is delivered to the ball-screw body from this stage portion.In addition, ball-screw 60 is supported with bearing 55 axles by the strong existing known support of thrust loading at the rear side of this prolongation 60a, simultaneously, more by the position at rear belt wheel 72 is being installed than this axle bearing position.Their installation site is fixed in belt wheel 72, support by the dividing bush of suitable length with bearing 55 and blade of a sword shape parts 62.In addition, these belt wheels or blade of a sword shape parts are only stopped by key and stop operating.
Especially, blade of a sword shape parts 62 form the plane identical with the end face of this matched moulds pressure head with the end face 62a of matched moulds pressure head side, and its back side 62b is formed taper seat, make the wall thickness of its central side constitute thicker wall.In addition, the end face 62a of this matched moulds pressure head side forms at radial direction and has the to a certain degree punctured disk shape of width.In addition, blade of a sword shape parts 62 with the chimeric endoporus of ball-screw 60 in the keyway that forms, avoid being configured in the stage portion side near the matched moulds pressure head side.All be in order to bear powerful mold clamping force.In addition, also can not form the plane with the matched moulds pressure head side end face 62a of matched moulds pressure head 50 butts, can be processed into with replacing and carry out the uniformly-spaced male and fomale(M﹠F) of groove processing, form and more be difficult to the face that slides.
Matched moulds pressure head 50 is comprised of the 50b of bar section of the piston portion 50a that bears hydraulic pressure and rearward extension.For example shown in the figure, matched moulds cylinder body 51 constitutes the single action cylinder body that only has the matched moulds side 51a of grease chamber, is communicated with the supply port of the action oil that diagram omitted in this matched moulds side grease chamber.The spline parts 52 that matched moulds pressure head 50 is stopped operating more specifically are the vertical pins 52 that is located on the cylinder body body 51, and piston portion 50a slides relatively.
Periphery in the movable platen side end face of matched moulds pressure head 50, one is installed the accessory 56 of the external diameter that enlarges as required movable platen, in order to easily be pressed into mechanism's 53 pushings.And this pressing mechanism 53 is loaded into as the Compress Spring 53 of this accessory 56 of pushing.Compress Spring 53 is a plurality of by uniformly-spaced burying underground at porose ledge 20b, and the pressing-in force that this Compress Spring produces adds up to and surpasses the mould opening force that is applied on the ball-screw 60 or the degree of mold closing power, and sets for less than mold clamping force.
The structure of removable earth's axis rotating bearing ball leading screw 60 is following formation more specifically.That is, in the structure of axle rotating bearing ball leading screw 60, known support is fixed in the bearing cage spare 58 with bearing 55, and this bearing cage spare is accommodated in limiting part 54 movably.Bearing cage spare 58 is used the outer ring of bearing 55 by two parts clampings and fixed support.Limiting part 54 is the cartridge units that form hole with the level, forms movably space of bearing cage spare 58 when constituting on being fixed in cylinder body body 51 between this cylinder body body of this Kong Zaiyu.In addition, form a plurality of shallow slots as being used for lubricated oil groove in the periphery of bearing cage spare 58, can seek the reduction of the resistance to sliding of bearing cage spare 58 relative cylinder body bodies 51.
Form the effective diameter D of matched moulds pressure head side end face 62a of the blade of a sword shape parts 62 of punctured disk, the addition that roughly is expressed as the external diameter of this punctured disk and internal diameter is average.For this effective diameter D, just can if wish to satisfy following relation.That is, this effective diameter D forms helical pitch (pitch) P of relative ball-screw above roughly (η/μ π) external diameter doubly is just passable.
That is, D/P＞η/μ π.
At this, coefficientoffrictionμ is the coefficient of friction of the bearing surface of blade of a sword shape parts 62 and matched moulds pressure head 50.Reverse efficiency η is the efficient when converting rectilinear motion to rotational motion, is the coefficient by the lead angle decision of ball-screw.
Roughly following derivation of above-mentioned multiplying power (ratio).At first, the rotating torque T1 that when the ball-screw of helical pitch P bears mold clamping force F, produces at ball nut, take η as reverse efficiency, then
T1＝ηFDP/2πD＝ηFP/2π。
On the other hand, the moment of friction T2 (braking moment) that is produced at the bearing surface of blade of a sword shape parts 62 and matched moulds pressure head 50 by mold clamping force F is when the hypothesis coefficient of friction is μ, when effective diameter is D, then
T2＝μFD/2。
Therefore, because moment of friction is when being T2=T1 consistent with rotating torque the time, so become
ηFP/2π＝μFD/2，
As a result, derive D/P=η/μ π.
Value becomes for example following value more specifically.Generally, the coefficient of friction of mutual even surface between the quenching steel can be not little than 0.05 even for example adhere to oil film yet.In addition, the reverse efficiency of lead angle 3 degree degree is about 90%.Therefore become,
D/P＝5.73。
If major diameter of thread is 50mm, helical pitch is 16mm, then the effective diameter D of rubbing surface surpasses about 92mm, is exactly fully real value.
In the occasion that consists of like this, the braking moment (being above-mentioned moment of friction) that produces between matched moulds pressure head 50 and blade of a sword shape parts 62 during matched moulds is conscientiously greater than the rotating torque that produces between ball-screw 60 and ball nut 61.Therefore, the load that applies between ball-screw 60 and ball nut 61 does not comprise dynamic load, becomes stable static load, can be selected to ball-screw the ball-screw of the path of low rated load, can improve the screw thread life-span simultaneously yet.
The mold closing mechanism of above formation carries out die opening and closing, matched moulds as shown in Figure 3.In addition, the figure of the upside of the center line of Fig. 3 represents the state in the die opening and closing, and the figure of its downside represents the state in the matched moulds.
At first, the figure of the first half of Fig. 3 remarked additionally.When die opening and closing, the matched moulds pressure head 50 that is pushed by pressing mechanism 53 rearward pushes bearing cage spare 58 in limiting part 54, remain on it and retreat on the limit positions.Therefore, the gap M between the bearing cage spare 58 of this moment and the aft bulkhead of matched moulds cylinder body 51 represents bearing cage spare 58 advanceable amount of movements, namely represents the amount of movement that limiting part 54 relative bearing cage spares 58 can retreat.In addition, the specified gap L between matched moulds pressure head 50 and the blade of a sword shape parts 62 become matched moulds pressure head 50 with bearing cage spare 58 retreat into bearing cage spare 58 retreat limit positions the time gap that occurs.This specified gap L is so long as 0.3mm is just enough to about the 0.5mm.In the present invention, owing to can make the L shaped Cheng Dexiao of this specified gap, can shorten the time that reaches matched moulds pressure head 50 and blade of a sword shape parts 62 butts when switching to matched moulds.This helps the high speed of the change action from the mold closing to the matched moulds.Certainly, although as basic structure of the present invention, not need for the structure of transmitting clamping pressure ground and switch the pressure transfer device that the machinery card takes off be the most effective to this high speed, above-mentioned feature also is important under recent shaping circulates the situation that shortens to the limit.
Below, the figure of the latter half is remarked additionally.Oppositely platen 20 is mainly rearward retreated the distance of matched moulds amount by the extension of pull bar 3 when matched moulds.This retreats is the amount of retreating of limiting part 54 relative bearing cage spares 58, embodies as distance N.At this, owing to constituting apart from M＞apart from N, so allow in the nature of things retreating of reverse platen 20 relative bearing cage spares 58.In addition, at this moment, ball-screw 60 or action axle 31 also shrink certainly slightly, but its distance can be ignored.Therefore, this matched moulds amount N is as the usually elongation representative of pull bar.
So servo motor 40 rotates control ball-screw 60, and the ball nut 61 that is threadedly engaged with it is moved, make movable platen 30 mobile with action axle 31, thereby carry out die opening and closing.At this moment, pressing mechanism 53 usefulness surpass the pressing-in force pushing matched moulds pressure head 50 of die opening and closing power, and the bearing cage spare 58 that is pushed to this matched moulds pressure head remains on it and retreats on the limit positions in limiting part 54.Its result is because these matched moulds pressure head 50 relative blade of a sword shape parts 62 are kept the state that leaves specified gap L, so ball-screw 60 is not rotated control with blade of a sword shape parts 62 with not interfering.
On the other hand, the pressing-in force ground that bears the matched moulds pressure head 50 opposing pressing mechanisms 53 of mold clamping force advances, and pushing blade of a sword shape parts 62 also push ball nut 61 and action axle 31, thereby carry out matched moulds.At this moment, the brake force by the frictional force that produces between matched moulds pressure head 50 and blade of a sword shape parts 62 forms stops the rotation of ball-screw 60.In addition, along with advancing of matched moulds pressure head 50, bearing cage spare 58 leaves matched moulds pressure head 50, supports with bearing 55 and does not bear the matched moulds load.And along with the extension of the pull bar 3 that is formed by mold clamping force, oppositely platen 20 relative bearing cage spares 58 retreat the distance about equally with matched moulds amount N.
According to the mold closing mechanism of the present invention of above formation, because the action axle 31 of movable platen 30 supports guiding by sliding bearing 32 in the pilot hole 20a of the porose ledge 20b of reverse platen 20, so the grazing of die opening and closing action becomes high accuracy.And, because this movable platen is by the sliding part supporting of two positions leaving of pull bar 3 and sliding bearing 32, so the grazing of this die opening and closing action all is constant at mold closing position, die sinking position.And, because the porose ledge 20b of reverse platen 20 and action axle 31 all are high rigidity, so can guarantee the grazing that rigidity is high.According to the grazing of this high rigidity, even such as the asymmetrical occasion about the metal die center such as the chimeric bad generation of guide finger etc., metal die can perk yet and grazing is further worsened.In addition, the normal load that is formed by rotation transfer mechanism 70 can not be applied to ball-screw 60, bear on the position of compression load of blade of a sword shape parts 62 or ball nut 61 sides.In addition, because this rotation transfer mechanism 70 is only by the simple formation of belt wheel 72, so do not give the danger of ball-screw 60 with rotational vibrations by accumulations such as the rigidity shortcoming of parts or concentricity are bad fully.In addition, because constituting, ball nut 61 is fixed on the action axle 31 that does not rotate, so can not give the lubricated obstacle that brings.In addition, because the action that matched moulds pressure head 50 and blade of a sword shape parts 62 leave specified gap L during die opening and closing only undertaken by pressing of forming of the pressing mechanism 53 as spring, so become simple for formation and the control of these departure motions.
Certainly, also ball-screw 60 can be arranged to the ball-screw of path of the low rated load of relative static load.This is that the braking moment that is produced by frictional force between the two is suppressed at the cause of the rotating torque that produces on this ball-screw when pressing blade of a sword shape parts 62 because of the matched moulds pressure head 50 that stops operating when matched moulds.
In addition, when matched moulds, because bearing cage spare 58 is released and can moves limiting part 54 from the state with matched moulds pressure head 50 butts, so mold clamping force can't help to support with bearing 55 burdens.In addition, because matched moulds pressure head 50 leaves with blade of a sword shape parts 62 when die opening and closing, be mould opening force or mold closing power so be applied to the power that supports with bearing 55.Therefore, can to bear the die opening and closing power especially less than mold clamping force with bearing 55 just passable as long as support.
Mold closing mechanism of the present invention also can constitute the such embodiment of Fig. 4.In this embodiment, matched moulds cylinder body 51 is constituted the bi-directional drive cylinder body that has the matched moulds opposition side 51b of grease chamber at the opposition side of the matched moulds side 51a of grease chamber.In this case, above-mentioned pressing mechanism 53 has replaced supplying with the hydraulic means that action oil produces pressing-in force to this matched moulds opposition side 51b of grease chamber.And when supplying with force feed to the matched moulds opposition side 51b of grease chamber during die opening and closing, matched moulds pressure head 50 is rearward pressed by the pressing-in force of having stated.Therefore, the departure motion of matched moulds pressure head 50 and blade of a sword shape parts 62 be not the elastic force by Compress Spring form by power but undertaken by the active force that hydraulic pressure forms, it is reliable that this control becomes.In addition, pressing-in force and stroke irrespectively become necessarily.In addition, form and only when die opening and closing, bear pressing-in force, can also reduce the amount that offsets with mold clamping force.
In addition, in another embodiment, also can append the safety device that when unusual, allows ball-screw 60 to retreat.At this, when what is called refers to when unusual that the mold closing action is stoped by unimaginable reason, for example be to set the situation of mutually conflicting, between ball-screw 60 and nut 61, producing impulsive force that makes between the metal die by the mistake of mold closing completing place.Be arranged on safety device in this case, for example constitute as shown in Figure 5.At this, represent state in the die opening and closing at the figure of the upside of the center line of Fig. 5, the figure of its downside represents the state in the matched moulds.
This safety device is provided with: fixedly the support of ball-screw 60 is with the bearing cage spare 58 of bearing 55; Limit in the above-described configuration between the limiting part 54 that this bearing cage spare 58 moves any one damper piston that all slides 59 with respect to these parts.Especially, in the periphery of damper piston 59 and the interior week of limiting part 54, produce the part with the level in gap when being formed on mutual combination, the gap between this part with the level forms the 59a of extrusion grease chamber that supplies with hydraulic operation oil.And the projected area of the die opening and closing direction of the 59a of grease chamber is pre-formed as described below.That is, damper piston 59 is forwards extruded under the action hydraulic coupling of regulation usually, in addition, sets above-mentioned projected area and hydraulic pressure in order to allow to retreat when unusual.In addition, the abutment portion 59b with the level that retreats limit positions of restriction bearing cage spare 58 when the periphery of interior week of damper piston 59 and bearing cage spare 58 forms mutual combination.
According to such formation, when common die opening and closing, because relatively be positioned at the damper piston 59 of the limit positions of advancing, bearing cage spare 58 is positioned at and retreats limit positions, so support remains on this with bearing 55 relative limiting parts 54 and retreats limit positions, in addition, when unusual, because bearing cage spare 58 retreats with damper piston 59 together relative limiting part 54, so relative limiting part 54 retreats when allowing to support with bearing 55 unusually.In addition, the retreating of the limiting part 54 relative bearing cage spares 58 that produce during for thereafter matched moulds, formed by mold clamping force, the same permission do not containing damper piston 59 retreating in consisting of.This is owing to stopping at damper piston 59 and to advance limit positions and bearing cage spare 58 stops under the state that retreats limit positions, and the cause that retreats of limiting part 54 only occurs.According to such formation, can append security function, that is, produce the moment permission threaded integral that impacts in the threaded portion of ball-screw 60 when unusual and retreat, cushion its impact.
In addition, in another embodiment, feed screw mechanism also can be made of the screw mechanism that comprises existing known trapezoidal screw or square leading screw.In this case, ball-screw is replaced by trapezoidal screw (diagram is omitted), and ball nut is replaced by the nut (diagram is omitted) that is threadedly engaged with thereon.And leading screw is made of in order to do not kill filling lubricating oil between these parts different materials with nut certainly.Because this adopts the screw mechanism of sample, because flank becomes ladder plane, so bear the area change of load, improved withstand load.In addition, when dynamic die opening and closing, keep the lubricant effect between leading screw and the nut, in addition, when static matched moulds, play the action effect that increases the friction between these parts.Therefore, above-mentioned screw mechanism can reduce the effective diameter of blade of a sword shape parts.
Industrial applicibility
The formation of above mold closing mechanism can adopt in requiring the precision pressure machinery of high accuracy and high speed.Can realize to the switching of the mould assembling action of the high-precision grazing of die opening and closing and high response.And, the hydraulic means that comprises the matched moulds pressure head is for example made the drive unit that the drive unit that formed by electromagnetic force or piezoelectricity sub-prime form, make simultaneously and reduce the afore mentioned rules gap L, carry out the device that switches to the matched moulds of high response more.
Claims (6)
1. the mold closing mechanism of an injection (mo(u)lding) machine (1), the movable platen (30) that has fixed platen (10), reverse platen (20) and between them, move, utilization drives the feed screw mechanism that rotates by servo motor (40) and carries out the mould switching, utilizes the hydraulic means that comprises matched moulds pressure head (50) to carry out matched moulds; It is characterized in that,
Described servo motor and described matched moulds pressure head are located at described reverse platen side, described feed screw mechanism consists of by the ball-screw (60) that is supported by axle in described reverse platen side with at the ball nut (61) that described movable platen side is fixed, this ball-screw more is being combined with described servo motor via rotation transfer mechanism (70) by on the position of die sinking direction side than its axle bearing position, described movable platen has to the side-prominent action axle (31) of described reverse platen, at the front end of this action axle described ball nut and sliding bearing (32) are installed, and the heart has the hollow hole (31a) that allows described ball-screw to enter therein, described reverse platen has the porose ledge (20b) that is formed with for the pilot hole (20a) of the described sliding bearing of sliding bearing, make the cylinder body body of the matched moulds cylinder body (51) of described matched moulds pressure head advance and retreat with formation, in this matched moulds cylinder body, spline parts (52) stop the rotation of described matched moulds pressure head, in addition, pressing mechanism (53) utilizes the above pressing-in force of die opening and closing power to press this matched moulds pressure head and make it to retreat, in addition, the position of the described matched moulds pressure head butt that described ball-screw also advances with matched moulds the time has blade of a sword shape parts (62), and the support that built-in axle supports described ball-screw can be housed among the limiting part (54) of the rear end of being fixed in described cylinder body body movably with the bearing cage spare (58) of bearing (55);
When die opening and closing, under the effect of described pressing mechanism to the described pressing-in force of described matched moulds pressure head, its Limitation Of Movement position is pressed and retreated into to described bearing cage spare by this matched moulds pressure head, described blade of a sword shape parts are maintained on the position of leaving this matched moulds pressure head specified gap, in addition, when matched moulds, described matched moulds pressure head is resisted described pressing-in force and is pressed progressively described blade of a sword shape parts, and leave described bearing cage spare, this bearing cage spare discharges load among described limiting part, and this reverse platen retreats the degree suitable with the matched moulds amount.
2. the mold closing mechanism of injection (mo(u)lding) machine as claimed in claim 1, it is characterized in that, the effective diameter D of the bearing surface of described blade of a sword shape parts and described matched moulds pressure head, be the reverse efficiency of μ, this ball-screw when being η at the coefficient of friction of establishing this bearing surface, form with respect to the helical pitch P of described ball-screw and surpass roughly η/μ π external diameter doubly.
3. the mold closing mechanism of injection (mo(u)lding) machine as claimed in claim 2, it is characterized in that, described matched moulds cylinder body is made of the single action cylinder body that only has matched moulds side grease chamber (51a), and described pressing mechanism is by Compress Spring (53) formation of utilizing described pressing-in force to press described matched moulds pressure head and make it to retreat to the die sinking direction.
4. the mold closing mechanism of injection (mo(u)lding) machine as claimed in claim 2, it is characterized in that, described matched moulds cylinder body is made of the bi-directional drive cylinder body with matched moulds side grease chamber (51a) and these two grease chambeies, matched moulds opposition side grease chamber (51b), and described pressing mechanism is by utilizing described pressing-in force to press described matched moulds pressure head and the hydraulic means that makes it to retreat consists of in the die sinking direction by supply with force feed to this matched moulds opposition side grease chamber.
5. such as the mold closing mechanism of claim 3 or 4 described injection (mo(u)lding) machines, it is characterized in that, described mold closing mechanism also is included in the safety device that allows described ball-screw to retreat when unusual, and this safety device comprises any damper piston that all slides (59) in relative these parts between described bearing cage spare and described limiting part;
In the periphery of this damper piston and the interior week of this limiting part, produce the part with the level in gap when being formed on mutual combination, and, the mutual gap of this part with the level consists of the extrusion grease chamber (59a) that supplies with hydraulic operation oil, supply with hydraulic operation oil by extrude the grease chamber to this, so that this damper piston forwards extruded usually the time, and when unusual, be allowed to retreat; In addition,
In the interior week of this damper piston and the periphery of this bearing cage spare, limit the abutment portion with the level (59b) that retreats limit positions of this bearing cage spare when being formed on mutual combination.
6. such as the mold closing mechanism of claim 3 or 4 described injection (mo(u)lding) machines, it is characterized in that, described feed screw mechanism is made of the screw mechanism that comprises trapezoidal screw or square leading screw.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP188494/2007 | 2007-07-19 | ||
| JP2007188494 | 2007-07-19 | ||
| PCT/JP2008/062558 WO2009011300A1 (en) | 2007-07-19 | 2008-07-11 | Mold clamping device for injection molding machine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101594972A CN101594972A (en) | 2009-12-02 |
| CN101594972B true CN101594972B (en) | 2013-03-06 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN200880001388XA Active CN101594972B (en) | 2007-07-19 | 2008-07-11 | Mold clamping device for injection molding machine |
Country Status (5)
| Country | Link |
|---|---|
| JP (1) | JP4565050B2 (en) |
| KR (1) | KR101241850B1 (en) |
| CN (1) | CN101594972B (en) |
| HK (1) | HK1137386A1 (en) |
| WO (1) | WO2009011300A1 (en) |
Families Citing this family (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP5474511B2 (en) * | 2009-05-15 | 2014-04-16 | 株式会社木村工業 | Hybrid pressure molding equipment |
| KR101121383B1 (en) * | 2011-06-07 | 2012-03-09 | 최병옥 | Hub bolt use pressure device |
| CN103182769A (en) * | 2013-03-24 | 2013-07-03 | 北京化工大学 | All-electric superspeed injection machine |
| JP5941122B2 (en) | 2014-11-06 | 2016-06-29 | ファナック株式会社 | Injection member mounting structure of injection molding machine |
| CN104369332B (en) * | 2014-11-21 | 2015-08-26 | 襄阳万联科工贸有限公司 | A kind of by fan-cooled injection mold apparatus matched moulds mould-opening equipment |
| CN104309082B (en) * | 2014-11-21 | 2016-05-04 | 宁波双利智能科技有限公司 | A kind of injection mold apparatus matched moulds die-sinking device of tightness adjustable |
| CN104441512B (en) * | 2014-11-21 | 2016-11-02 | 慈溪欧新生物科技有限公司 | A kind of injection mould closing mould-opening equipment containing rack-and-pinion and roller |
| CN104309083B (en) * | 2014-11-21 | 2016-04-06 | 宁波双利智能科技有限公司 | The injection moulding device containing rack-and-pinion is adopted to carry out the method for matched moulds die sinking |
| JP6522363B2 (en) * | 2015-02-19 | 2019-05-29 | スチールプランテック株式会社 | Mold vibrator |
| CN106925747A (en) * | 2017-04-25 | 2017-07-07 | 苏州三基铸造装备股份有限公司 | Die casting machine molds safety device |
| CN108890997A (en) * | 2018-07-13 | 2018-11-27 | 浙江申达机器制造股份有限公司 | A kind of electro-hydraulic mixed injection molding machine folding mode structure and its rapid mould opening-closing control method |
| JP6967638B1 (en) * | 2020-08-27 | 2021-11-17 | 株式会社ソディック | Molding device for injection molding machine |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1272077A (en) * | 1998-08-25 | 2000-11-01 | 沙迪克株式会社 | Mold clamping device for injection molding machines and mold-opening control method thereof |
Family Cites Families (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS61237617A (en) * | 1985-04-13 | 1986-10-22 | Meiki Co Ltd | Mold clamping device in injection molding machine |
| JPS63242618A (en) * | 1987-03-31 | 1988-10-07 | Meiki Co Ltd | Mold clamping device in injection molder |
| JPH0771807B2 (en) * | 1988-08-08 | 1995-08-02 | 三菱重工業株式会社 | Mold clamping device |
| JP2521591B2 (en) * | 1991-05-07 | 1996-08-07 | 株式会社ソディック | Electro-hydraulic mold clamping device for injection molding machine |
| JPH11115009A (en) * | 1997-10-09 | 1999-04-27 | Sodick Co Ltd | Mold clamping device for injection-molding machine |
| JP3600167B2 (en) * | 2000-09-29 | 2004-12-08 | 浅之助 千坂 | Injection compression molding method |
| JP3917480B2 (en) * | 2002-07-15 | 2007-05-23 | 株式会社名機製作所 | Mold clamping device and method of operating the same |
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2008
- 2008-07-11 WO PCT/JP2008/062558 patent/WO2009011300A1/en active Application Filing
- 2008-07-11 CN CN200880001388XA patent/CN101594972B/en active Active
- 2008-07-11 KR KR1020097016884A patent/KR101241850B1/en active IP Right Grant
- 2008-07-11 JP JP2009523628A patent/JP4565050B2/en active Active
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1272077A (en) * | 1998-08-25 | 2000-11-01 | 沙迪克株式会社 | Mold clamping device for injection molding machines and mold-opening control method thereof |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2009011300A1 (en) | 2009-01-22 |
| KR20100031494A (en) | 2010-03-22 |
| CN101594972A (en) | 2009-12-02 |
| JP4565050B2 (en) | 2010-10-20 |
| HK1137386A1 (en) | 2010-07-30 |
| JPWO2009011300A1 (en) | 2010-09-24 |
| KR101241850B1 (en) | 2013-03-12 |
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