CN107191236A - The hydraulic valve of piston for the hydraulic valve of camshaft phase adjuster and the camshaft phase adjuster for camshaft - Google Patents
The hydraulic valve of piston for the hydraulic valve of camshaft phase adjuster and the camshaft phase adjuster for camshaft Download PDFInfo
- Publication number
- CN107191236A CN107191236A CN201710119961.8A CN201710119961A CN107191236A CN 107191236 A CN107191236 A CN 107191236A CN 201710119961 A CN201710119961 A CN 201710119961A CN 107191236 A CN107191236 A CN 107191236A
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- China
- Prior art keywords
- piston
- hydraulic valve
- opening
- check
- valves
- Prior art date
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- 238000005325 percolation Methods 0.000 claims abstract description 54
- 239000012530 fluid Substances 0.000 claims abstract description 52
- 125000006850 spacer group Chemical group 0.000 claims abstract description 40
- 238000000926 separation method Methods 0.000 claims description 5
- 230000000694 effects Effects 0.000 claims description 4
- 239000002828 fuel tank Substances 0.000 description 9
- 238000002485 combustion reaction Methods 0.000 description 6
- 238000010276 construction Methods 0.000 description 6
- 230000008901 benefit Effects 0.000 description 5
- 238000005516 engineering process Methods 0.000 description 4
- 238000004519 manufacturing process Methods 0.000 description 4
- 241001672694 Citrus reticulata Species 0.000 description 3
- 230000006698 induction Effects 0.000 description 3
- 230000009467 reduction Effects 0.000 description 3
- 230000002411 adverse Effects 0.000 description 2
- 230000008859 change Effects 0.000 description 2
- 238000000354 decomposition reaction Methods 0.000 description 2
- 230000010354 integration Effects 0.000 description 2
- 230000002000 scavenging effect Effects 0.000 description 2
- 238000006243 chemical reaction Methods 0.000 description 1
- 230000006837 decompression Effects 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 238000007599 discharging Methods 0.000 description 1
- 239000004744 fabric Substances 0.000 description 1
- 230000002349 favourable effect Effects 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000036632 reaction speed Effects 0.000 description 1
- 230000035484 reaction time Effects 0.000 description 1
- 230000000284 resting effect Effects 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
- F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
- F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
- F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
- F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
- F01L2001/34423—Details relating to the hydraulic feeding circuit
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
- F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
- F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
- F01L2001/3445—Details relating to the hydraulic means for changing the angular relationship
Abstract
The present invention relates to the piston of the hydraulic valve for camshaft phase adjuster, wherein the piston (4) is configured to hollow cylinder, and wherein the piston can be axially movable in the central opening (5) that the first longitudinal axis (3) of the housing (2) along hydraulic valve (1) extends, the wherein especially working joint (A of the housing, B) according to the opening in place of the piston and closure, and wherein the piston undesirably flows out to the percolation opening (29 for being associated with working joint of the piston from the inner space (9) of the piston in order to avoid the hydraulic fluid for the piston that flows, 30) and with check-valves (25, 26).According to the present invention, the piston is configured to make to be contained in the inner space of the piston towards the check-valves that its inner space (9) are opened, the check-valves by means of being arranged in described two check-valves between spacer element (27) it is fixed.In addition, the present invention relates to the hydraulic valve of the camshaft phase adjuster for camshaft.
Description
Technical field
The present invention relates to the hydraulic valve as described in the preamble, for camshaft phase adjuster according to claim 1
Piston and the hydraulic valve according to camshaft phase adjuster described in claim 10, for camshaft.
Background technology
Hydraulic valve for the camshaft phase adjuster of the camshaft of internal combustion engine is well-known.The hydraulic valve tool
Have can in hydraulic pressure valve housing axially activity piston, by means of the piston adjust camshaft phase adjuster hydraulic pressure add
Carry.Hydraulic valve has a variety of structure types.The housing is configured to hollow cylinder.The piston is also configured as sky
Heart cylinder.The camshaft phase adjuster is hydraulically adjusted by means of the in place of the piston that can flow and is constructed in shell
The corresponding release of joint at body closes to carry out.
Following hydraulic valves as known to the A1 of open source literature DE 10 2,013 104 573 and the A1 of DE 10 2,013 104 575,
It has a supply joint at shell end, and mode is that can cause directly becoming a mandarin and therefore for the piston being contained in housing
Cause the linearity loading for the hydraulic fluid that the piston supplies by means of supply joint.The piston has the outer of complexity
Portion's geometrical construction, so as to avoiding the adverse current from working joint to piston.
Following hydraulic valves are learnt by the A1 of open source literature US 2014/0311333 and the A1 of US 2014/0311594, it has
Construct the check-valves at the side face of piston.Thus, or for the accommodating and fixed check-valves need the shell of high cost
Body is designed, or the housing be configured to multi-piece type and need high assembly cost.The piston be configured to multi-piece type and
And each component must be engaged concentrically, thus, based on avoiding eccentric throw in pressing parts, it is necessary to the assembling of high cost.
Another hydraulic valve as known to the A2 of open source literature EP 2 966 272, there is so-called center to interlock for it.By
In the interlocking fit being extraly arranged in hydraulic pressure valve housing, the piston has complicated exterior geometry.
The content of the invention
The task of the present invention is to provide the piston of the hydraulic valve for camshaft phase adjuster, and it is cost-effectively
It is reliable while manufacture.Another task of the present invention is to provide a kind of hydraulic valve, and it can cost-effectively be manufactured.
According to the present invention, the task passes through hydraulic pressure feature, for camshaft phase adjuster with claim 1
The piston of valve is completed.The solution of another task passes through feature, for camshaft with claim 10
The hydraulic valve of camshaft phase adjuster is realized.Including according to the suitable and important improvement project, preferably of the present invention
Design is provided in each dependent claims.
Piston according to the hydraulic valve for camshaft phase adjuster of the present invention is configured to hollow cylinder.It is described
Piston can be axially movable in the central opening of the first longitudinal axis extension along the hydraulic pressure valve housing, wherein especially described shell
The working joint of body is opened and blocked by means of piston according to the in place of piston.The piston is in order to avoid the piston that flows
Percolation opening that hydraulic fluid undesirably flows out to piston from the inner space of piston, being associated with working joint and with only
Return valve.According to the present invention, piston is constructed so as to be contained in the inside of the piston towards the check-valves that its inner space is opened
In space, the check-valves is fixed by means of the spacer element between being arranged in described two check-valves.
Arrangement of the check-valves in the inner space of piston causes the piston to be manufactured in the way of cost advantages
Its exterior geometry, wherein being avoided the overflow of the non-original idea of the hydraulic fluid by means of the check-valves.
The check-valves is provided for preventing the mutual percolation of the non-original idea of connection opening.This especially can be in pulsed hydraulic pressure pressure
Occur in the case of power.This explanation, otherwise the housing must make each working joint have two connection openings, otherwise it is described
Piston designs with the channel-shaped geometry that expends, so as to can synchronously realize that the balancing gate pit of the camshaft phase adjuster is filled out
Fill and empty.
The spacer element is used to fix the check-valves and ensure the check-valves in the inner space of piston
Each other away from.Therefore, the complex internal geometry of the piston is avoided by means of spacer element, in order to fix the non-return
Valve, the complex internal geometry is required.It is contained in by the check-valves in inner space and by means of interval
Element is fixed, and the piston can be made into integration.Therefore the manufacture of the cost advantages of the piston can be realized, because cancelling therewith
The assembling of the consuming of piston.
In a kind of design, the spacer element has cross or star-shaped cross-section.Therefore, flow channel is so
It can construct in spacer element, i.e., cause hydraulic fluid space internally since being associated with the percolation opening of working joint
In targetedly turn to.If for example described piston is in place in order to fill the balancing gate pit being connected with working joint, pass through
The hydraulic fluid that supply joint is flowed into begins to flow to be associated with the percolation opening of the working joint from inner space.By another
Working joint, the hydraulic fluid is flowed to interior from its balancing gate pit for being associated with the working joint by check-valves at least in part
Portion space.By means of constructing the flow channel in spacer element, the hydraulic fluid is directly directed to wearing for the working joint
Stream opening, the filling is carried out by the working joint.The hydraulic fluid can not be climing in whole inner space first
Prolong, but since the percolation opening for the working joint for being associated with balancing gate pit to be evacuated, be directly directed to be associated with it is to be filled
The percolation opening of the working joint of balancing gate pit.It is achieved in Fast Filling and therefore shortens the anti-of the camshaft phase adjuster
Between seasonable.
In order to aid in the spacer element to the introducing of piston in period of assembly, the spacer element is at least one side
There is hypotenuse or the lateral edge to be configured to rounding for edge.
Have proven to be especially suitable for for assembling hydraulic valve, the hypotenuse is configured with the angle that numerical value is 15 °.More
Big angle may cause the inclination of spacer element and block in assembling.Angle with more fractional value, especially less than 10 °
The introducing of further improved spacer element is not brought.
In other designs, the outside of the spacer element and the interior diameter of piston are matchingly constructed.Thus, a side
Face can advantageously cause the as complete as possible of the flow channel constructed by means of spacer element to separate.On the other hand, institute
Spacer element is stated to be more securely held in piston due to the mantle friction in period of assembly.
The second aspect of the present invention is related to the hydraulic valve of the camshaft phase adjuster for camshaft.The hydraulic valve bag
The piston for including housing and can be axially movable in the central opening of the first longitudinal axis extension along the housing.Especially described housing
Working joint according to the opening in place of piston and closure.The piston in order to avoid the piston of flowing hydraulic fluid from work
Percolation opening that the inner space of plug undesirably flows out to piston, being associated with working joint and with least one non-return
Valve.According to the present invention, the piston according to one of claim 1 to 9 it is described construct.
Hydraulic valve according to the present invention is flexible when changing percolation opening relative to piston path and therefore can be
Such as each working joint has the company for the connection opening that each working joint is reduced in the hydraulic valve of at least two connection openings
Connect open amount.This is based on the description below, i.e., having according to the hydraulic valve of the present invention can be by means of the movable check-valves of piston, institute
Check-valves is stated relative to connection opening activity, on the contrary in the hydraulic valve according to prior art, the check-valves is fixed.
In addition, the piston can be used for hydraulic valve due to its exterior geometry simply manufactured with its basic geometry
Different constructional variants, so as to be avoided that the design work of consuming.Therefore, the hydraulic valve can be manufactured cost-effectively.
In the design according to the hydraulic valve of the present invention, the supply joint arrangement tubular structure housing the
An end portion, the piston is thus, it is possible to advantageously directly become a mandarin and become a mandarin in the case where the flowing of lossless reduction is turned to.This
It is required that reaction time or the reaction speed of the camshaft phase adjuster.
In another design, the hydraulic valve has other connection openings, to adjust with center interlocking
Camshaft phase adjuster.Compared with the hydraulic valve according to prior art, it can be seen that according to the excellent of hydraulic valve of the invention
Point is that its camshaft phase for being provided for interlocking with center in the way of the structure space of largely reduction is adjusted
Save device.Therefore compact camshaft phase adjuster can be realized, it has center interlocking relative to according to prior art
Camshaft phase adjuster for have reduction structure space demand.
Brief description of the drawings
Further advantage, feature and the details of the present invention by preferred embodiment the description below and draw with reference to the accompanying drawings.
Feature and combinations of features above described in explanation and next described in the description of the drawings and/or only mark in the accompanying drawings
The feature and combinations of features shown can not only be used in the combination of respective specified and can be used in other combinations or make alone
With without departing from the framework of the present invention.Identical or function identical element is equipped with identical reference.In order to it is very clear can
Capable, the element does not arrange its reference in all of the figs, but will not lose its relation.Wherein：
Fig. 1 with three-dimensional view show in the first embodiment be used for camshaft it is camshaft phase adjuster, according to
The hydraulic valve of the present invention,
Fig. 2 shows the hydraulic valve according to Fig. 1 with another three-dimensional view,
Fig. 3 illustrates the hydraulic valve according to Fig. 1 with vertical profile,
Fig. 4 shows the hydraulic valve according to Fig. 1 with decomposition view,
Fig. 5 shows the hydraulic valve at diverse location according to Fig. 1 with symbol view,
Fig. 6 illustrates the hydraulic valve in first position according to Fig. 1 with vertical profile,
Fig. 7 illustrates the hydraulic valve in the second place according to Fig. 1 with vertical profile,
Fig. 8 illustrates the hydraulic valve in the 3rd position according to Fig. 1 with vertical profile,
Fig. 9 a) spacer element according to hydraulic valve of the invention according to Fig. 1 is shown with three-dimensional view,
Fig. 9 b) with overlook illustrate according to Fig. 9 a) spacer element,
Fig. 9 c) with along secant IXc)-IXc) and section view illustrate according to Fig. 9 a) spacer element,
Fig. 9 d) illustrated with side view according to Fig. 9 a) spacer element,
Figure 10 shows the piston of the hydraulic valve according to Fig. 1 with three-dimensional view,
Figure 11 to have an X-rayed the piston illustrated according to Figure 10,
Figure 12 shows hydraulic valve in a second embodiment at diverse location with symbol view,
Figure 13 illustrates the hydraulic valve in first position according to Figure 12 with vertical profile
Figure 14 illustrates the hydraulic valve in the second place according to Figure 12 with vertical profile,
Figure 15 illustrates the hydraulic valve in the 3rd position according to Figure 12 with vertical profile,
Figure 16 illustrates the hydraulic valve in the 4th position according to Figure 12 with vertical profile,
Figure 17 shows the piston of the hydraulic valve according to Figure 12 with three-dimensional view；And
Figure 18 to have an X-rayed the piston illustrated according to Figure 17,
Embodiment
According to the present invention, for the camshaft phase adjuster not being shown in further detail for the camshaft not being shown in further detail
Hydraulic valve 1 construct in the first embodiment according to Fig. 1.Hydraulic valve 1 is configured to be contained in camshaft phase as central valve
In the rotor not being shown in further detail of position adjuster.That is in other words, hydraulic valve 1 is opened in the center of camshaft phase adjuster
Housed with least partly surrounding by the camshaft phase adjuster in mouthful.
Hydraulic valve 1 has the housing 2 for being configured to percolation.In order to carry out hydraulic pressure supply to the camshaft phase adjuster
Multiple joint A, B, P, T1, T2 are provided with housing 2.In housing 2, it can be axially moved along the first longitudinal axis 3 of hydraulic valve 1
Piston 4 is contained in the central opening 5 of housing 2.Housing 2 is in most cases configured to tubulose.
The camshaft phase adjuster allows to cause internal combustion engine during the operation for the internal combustion engine not being shown in further detail
The opening time of scavenging air valve and the change of shut-in time.Therefore, infinitely changing interior by means of the camshaft phase adjuster
The camshaft not being shown in further detail of combustion engine relative to the bent axle not being shown in further detail of internal combustion engine relative angular position, wherein
The camshaft is relative to crankshaft torsion.Due to the torsion of the camshaft, when the opening time point of the scavenging air valve and closing
Between put so passage, i.e., described internal combustion engine can provide its optimal efficacy in the case of corresponding rotating speed.
The stator not being shown in further detail of the camshaft phase adjuster is not torsionally more detailed with the camshaft
The driving wheel connection shown.At the inner side of stator base, the lath extended radially inwardly is so configured with regular intervals,
Gap is formed between each two adjacent laths.Stretch into and described be disposed with not being shown in further detail for the rotor with gap
The blade not being shown in further detail of rotor hub.The rotor hub has the quantity for the blade being consistent with the quantity in the gap.Cause
This, by means of the blade, each gap can be divided into Liang Ge balancing gate pits.In subspace, controllably drawn by means of hydraulic valve 1
Enter pressure medium, be usually hydraulic fluid.
Each working joint A, B are associated with balancing gate pit.In this way, first working joint 1 is associated with first pressure room, and
And the second working joint B is associated with second pressure room.In order to change the angle position between the camshaft and bent axle,
Make the pressure medium in first pressure room or while be pressurized in second pressure room, make the second pressure room or first press
Depressurize power room.The decompression is carried out by the first fuel tank connector T1 or the second fuel tank connector T2, wherein the hydraulic fluid
It can be flowed out by described fuel tank connector T1, T2.
Hydraulic valve 1 according to the present invention is drawn with sectional side elevation in figure 3.It is that piston 4 is configured to hollow cylinder and have
There are the first percolation opening 6, second percolation opening 7 and the 3rd percolation opening 8.Each percolation opening 6,7,8 is configured to completely penetrate through
Piston 4, so that the hydraulic fluid can begin through percolation opening 6,7,8 from the inner space 9 of piston 4 flows into working joint
With fuel tank connector A, B, T1, T2.Fluid to the adverse current for supplying joint P is prevented by first check-valve 10, the first check-valve cloth
Put in the region of the end 11 of housing 2, in housing 2 by means of locking element 12 position fix fluid filter 13 under
Trip.It is being configured between the check-valves 10 of ring check valve and fluid filter 13, flap (flow is equipped with shell 12
Disc) 14, the flap opening 15 of the flap can be closed by means of first check-valve 10.
First check-valve 10 is by means of the first pre-tensioning element 16 towards the on-load pressure of flap 4.That is in other words, in order to
The flap opening 15 is closed, is pressed by means of the first pre-tensioning element 16 towards flap 14.As long as flowing through supply joint P liquid
Press fluid that there is the prestressed pressure more than the first pre-tensioning element 16, first check-valve 10 is just lifted and institute from flap 14
State entrance passage 17 that hydraulic fluid enters piston 4 by flap opening 14, being connected with flowing with inner space 9.
For the locking and guiding of piston 4, the piston has at its first piston end 21 to be shown at least in part
Go out to enter the bolt shape induction element 18 of passage 17.It is contained in locking lid 19 to the interlocking of induction element 18, except the lock
Fixed and guiding, calibration of the locking lid for hydraulic valve 1.In addition, the locking lid 19 is used at described first pre-tensioner yuan
First pre-tensioning element is supported on the side constructed back on first check-valve 10 of part 16.The induction element 18 is rabbeted
Ground is arranged in the central cover gab 20 of locking lid 19.
The piston 4 is at the second piston end 28 that it is constructed back on first piston end 21 with not being shown in further detail
Actuator effectively connect.Have piston cap 22 in place at second piston end 28, the piston cap closed interior space 9 to prevent
Fluid stopping body overflows.Flowed out from the second working joint B, flow into the second fuel tank connector T2 fluid by being configured in housing 2 and piston 4
Between gap guide to the second fuel tank connector T2.
In addition, the actuator drift not being shown in further detail is rabbeted in the piston cap at piston cap 22 back on inside
At the capping 23 that space 9 is constructed, so as to make piston 4 be seated in central opening 5 by means of the actuator.For piston 4
Reliable to be provided with the second pre-tensioning element 24 in place, second pre-tensioning element is arranged between piston 4 and locking lid 19, in
In centre opening 5.
Hydraulic valve 1 according to the present invention has for the second check-valve 25 of the percolation of protection second opening 7 and for protecting
3rd check-valves 26 of the 3rd percolation opening 8, to prevent hydraulic fluid from described two percolation openings 7,8 to working joint A, B
Outflow, described second and the 3rd check-valves by constructing the first connection opening 29 or construction in housing 2 the in housing 2
Two connection openings 30 are connected in which can flow.For the fluid guiding and protection in place of described two check-valves 25,26, at them it
Between be disposed with spacer element 27.
The hydraulic valve 1 according to the first embodiment of the present invention is drawn with decomposition view in Fig. 4.
Fig. 5 shows hydraulic valve 1 at diverse location, according to the present invention with symbol view.Figure 5 illustrates symbol
The left part of number view show according to figure 6 illustrates piston 4 first position hydraulic valve 1 percolation.At described first
Place is put, the second working joint B is loaded with hydraulic fluid.That is in other words, the hydraulic fluid is begun flow through from supply joint P
The percolation opening of inner space 9 and first 6, the second connection opening that the first percolation opening release is connected with the second working joint B
30.In addition, the hydraulic fluid from the first working joint A at least partially through the first connection opening 29 and can pass through first
The opening of check-valves 25 flows into inner space 9, wherein the hydraulic fluid guides the first percolation opening 6 into by spacer element 27.
The hydraulic fluid continues through the second connection opening 30 and flows to the second working joint B therefrom.From the first working joint A outflows
The fluid other parts flow through first discharge passage 31 to construction housing 2 the 3rd connection opening 45 in, the row
Go out passage and channel-shaped is configured in the region of the second percolation opening 7, the 3rd connection opening is associated with the first fuel tank connector
T1.First discharge passage 31 is especially as seen from Figure 11.
It is described especially in Fig. 9 a) to Fig. 9 d) and in the one side of spacer element 27 that is shown specifically there is movement-oriented element
Function and the function on the other hand with spacer element.As especially in Fig. 9 c) in visibly, its have symmetrically intersect it is transversal
Face, this illustrate spacer element 27, along Fig. 9 b) secant IXc)-IXc) and section.
The fluid is matched somebody with somebody from the overflow of inner space 9 to corresponding connection opening 29,30 or corresponding joint A, B to fill
Belong to each joint A, B balancing gate pit, only carried out by the first percolation opening 6.Because in the present embodiment, the percolation is open
6 have four son openings, therefore the spacer element 27 includes four separation laths 32 being mutually arranged with right angle.Therefore, institute
State separation lath 32 to be designed as being configured with four flow channels in cylindrical interior space 9, so as to provide to per height opening
The fluid branch that percolation passes through the first percolation opening 6.Thus the reaction for filling corresponding balancing gate pit can largely be shortened
Time.
Separate lath 32 to be configured to cling at piston 4, adjacent inner space 9 inwall 33.In order that the fluid
Branch portion overflow to flow opening 6 corresponding sub- opening, separate lath 32 have recess 34.
In order to avoid the flow separation being likely to occur, the recess 34 its towards spacer element 27 the second longitudinal axis 35
There is the first radius R1 and at the outer edge 37 that it is constructed back on the second longitudinal axis 35 at the inner face edge 36 of construction
With the second radius R2.It is preferred that described two radiuses are for the reason for particularly manufacturing technology and size is identical.However, they
The corresponding of hydraulic valve 1 is adapted to use field and be configured to of different sizes.
In order to improve spacer element 27 to the introducing of inner space 9 when assembling hydraulic valve 1, the separation lath 32 is at it
There is hypotenuse 42 respectively, the hypotenuse has the angle [alpha] that numerical value is preferably 15 ° at lateral edge 38.
Spacer element 27 has the outside 43 with overall diameter D1 being constructed towards inwall 33, overarching, described outer straight
Footpath is configured to match the interior diameter DI1 of piston 4.In order to cause the favourable flow behavior of the fluid, the recess 34 it is interior
Face 44 has diameter D2 and therefore corresponding to the diameter D2 is matchingly designed as arch.
Generally, the spacer element makes flowing optimally by radius R1, R2 for being constructed and the face overarched 43,44
Formed, because at least reducing the unexpected interruption flowed and generally occurred within sharp edges.
In with the central section of the hydraulic valve 1 shown in symbol, hydraulic valve 1 the second place of piston 4 percolation with
Symbol is drawn, the second place correspond to figure 7 illustrates piston position.Connect in the second place without work
Head A, B percolation.
3rd position of piston 4 is drawn and relative with the symbol view of the percolation shown in the right part in Fig. 5 in fig. 8
Should.At the position, the first working joint A is loaded with hydraulic fluid.That is in other words, the hydraulic fluid is from supply joint
P begins flow through the percolation opening of inner space 9 and first 6, what the first percolation opening release can be connected with the first working joint A
First connection opening 29.In addition, the hydraulic fluid from the second working joint B can be at least partially through the second connection opening 30
And inner space 9 is flowed into by the opening of second check-valve 26, wherein the hydraulic fluid guides the into by spacer element 27
One percolation opening 6.The hydraulic fluid flows into the first working joint A from there through the first connection opening 29.
The second fuel tank flowed to by second discharge passage 39 from the other parts of the second working joint B fluids flowed out
Joint T2, the second discharge passage is configured to channel-shaped in the region of the 3rd percolation opening 8.Second discharge passage 39 is especially
As seen from Figure 11.In order to further illustrate, piston 4 is shown in Figure 10 and Figure 11.
Hydraulic valve 1 according to the present invention is also configured to the hydraulic valve 1 interlocked with so-called center, such as according to figure
12 to Figure 16 second embodiment is illustratively.So-called center interlocking is interpreted as the interlocking of rotor and stator, and it can
Cause in the case of without electric control.Therefore, except up to the present working joint A, B as known to first embodiment,
Hydraulic valve 1 also has other joints that can be flowed.Other joints, i.e. the first interlocking fit S and the second interlocking fit L, if
Put the interlock system for loading the camshaft phase adjuster.Described interlocking fit S, L are typically due to manufacturing technology and knot
The advantage of structure technology is arranged along the first longitudinal axis 3 of housing 2 in series with working joint A, B.Thus necessarily draw housing along its
The bigger extension size of first longitudinal axis 3.In other words that is, the hydraulic valve 1 and can contrast do not have center
The hydraulic valve 1 of interlocking, which is compared, has bigger structure length.
Figure 12 shows the hydraulic valve 1 according to the present invention with second embodiment, and it has with different shown in symbol
The so-called center interlocking of position.
The result of interlocking fit S, L arranged in series is that the longer impulse stroke of piston 4 or the extension of piston 4 are rushed
Journey.In order that flowed with meeting functional requirement for described joint A, B, T1, T2, S, L that camshaft is adjusted, the second working joint
B also needs to be equipped with extra percolation opening in piston 4, and it is referred to as the 4th percolation opening 40.According to working joint A, B
In place, the extra percolation opening can be also arranged to the first working joint A.This depends on the make of hydraulic valve 1.
In order to avoid being flowed the 4th percolation opening 40 from inner space 9, the percolation opening 40 is also equipped with non-return
Valve, i.e. the 4th check-valves 41.At this it shall be mentioned that the check-valves 25,26,41 being contained in piston 4 is configured to banding check-valves.
The left part of the symbol view drawn in fig. 12 with according to figure 13 illustrates piston 4 first position hydraulic pressure
The percolation of valve 1 is corresponding.In the first position, the first interlocking fit S is loaded with hydraulic fluid.That is in other words, institute
Hydraulic fluid is stated to begin flow through the percolation opening of inner space 9 and first 6 from supply joint P, flow through the 4th of construction in housing 2
Connection opening 46, the first interlocking fit S of inflow.Meanwhile, it is associated with described the two of the first working joint A and the second working joint B
Individual balancing gate pit is so emptied at least in part, i.e., described hydraulic fluid flows through working joint A, B from the balancing gate pit and it is attached troops to a unit
Connection opening 29,30, inner space 9 is flowed into the case where check-valves 25,26 is acted on and the first percolation is flowed through therefrom
Opening 6, flow to the first interlocking fit S.At the same time, the interlock system empties to the first fuel tank by the second interlocking fit L
Joint T1, second interlocking fit is associated with the 5th connection opening 47 in housing 2.
The lath 32 that separates of the spacer element 27 of second embodiment has three along the recessed of the arranged in series of the second longitudinal axis 35
Portion 34.In order to which the 3rd percolation opening 8 and the 4th percolation opening 40 can flow, this is required.This modification of spacer element 27
Advantage be, piston cap 22 and spacer element 27 can Construction integration, as its situation in current second embodiment that
Sample.Thus the assembling of piston 4 is simplified.
During deflection stage of the rotor relative to stator, in the deflection stage, the second working joint B pressure is associated with
Power room is filled with hydraulic fluid, and piston 4 is in place as shown in Figure 14.The hydraulic fluid is begun flow through from supply joint P
The percolation opening of inner space 9 and first 6, shown first percolation opening is connected in which can flow with the second working joint B, wherein discharging
Second connection opening 30.In addition, the hydraulic fluid from the first working joint A can be at least partially through the first connection opening 29
And inner space 9 is flowed into by the opening of first check-valve 25, wherein the hydraulic fluid guides the into by spacer element 27
One percolation opening 6.The hydraulic fluid further flows through the second connection opening 30, flows to the second working joint B therefrom.Remaining
Joint S, L blocked by means of piston 4
As long as not only having blocked the first working joint A but also having blocked the second working joint B, piston 4 is located in so-called resting position.
In addition, being referred to as the position of the 3rd position, figure 15 illustrates or draw in the second section in symbol view on the right
Go out.
For the first working joint A that flows, piston 4 is at the 4th position, wherein the first connection opening 29 is by the
One percolation opening 6 discharges.At the position, in the case where emptying is associated with the second working joint B balancing gate pit, matched somebody with somebody
Belong to the filling of the first working joint A balancing gate pit.The hydraulic fluid begins flow through inner space 9 and the from supply joint P
One percolation opening 6, shown first percolation opening is connected in which can flow with the first working joint A, wherein the connection opening of release first
29.In addition, the hydraulic fluid from the second working joint B at least partially through the second connection opening 30 and can pass through the 4th
The opening of check-valves 41 flows into inner space 9, wherein the hydraulic fluid by means of spacer element 27, pass through the 3rd check-valves 26
Guide the first percolation opening 6 into.The hydraulic fluid further flows through the first connection opening 29, flows to the first working joint therefrom
A.Remaining joint S, L is blocked by means of piston 4.
The hydraulic valve 1 according to the present invention is shown with 3rd embodiment in Figure 17 and Figure 18, wherein percolation 6,7,8 structures of opening
Cause long hole forms.Piston cap 22 in another locking element 48 of clamping loop type by means of being fixed on piston 4.
Claims (12)
1. the piston of the hydraulic valve for camshaft phase adjuster, wherein the piston (4) is configured to hollow cylinder, and
And central opening (5) axis that wherein described piston (4) can extend in the first longitudinal axis (3) of the housing (2) along hydraulic valve (1)
To activity, wherein in place opening and closure of the working joint (A, B) of especially described housing (2) according to the piston (4), and
Wherein described piston (4) does not expect in order to avoid the hydraulic fluid for the piston (4) that flows from the inner space (9) of piston (4)
Ground flows out to the percolation opening (29,30) for being associated with working joint (A, B) of piston (4) and with check-valves (25,26), it is special
Levy and be, the piston (4) is constructed so as to be contained in the work towards the check-valves (25,26) that its inner space (9) are opened
In the inner space (9) of plug, the check-valves by means of being arranged in described two check-valves (25,26) between spacer element
(27) it is fixed.
2. piston according to claim 1, it is characterised in that the spacer element (27) has cross or star transversal
Face.
3. piston according to claim 1 or 2, it is characterised in that the spacer element (27) separates with least one
Lath (32).
4. piston according to claim 3, it is characterised in that the separation lath (32) has recess (34).
5. piston according to claim 4, it is characterised in that the recess (34) has the inner face circumferentially bent.
6. the piston according to one of preceding claims, it is characterised in that the spacer element (27) is at least one side
There is hypotenuse (42) or the lateral edge (38) to be configured to rounding at face edge (38) place.
7. piston according to claim 6, it is characterised in that the hypotenuse has the angle (α) that numerical value is 15 °.
8. the piston according to one of preceding claims, it is characterised in that the outside (43) of the spacer element (27) with
The interior diameter (DI1) of piston (4) is matchingly constructed.
9. the piston according to one of preceding claims, it is characterised in that the spacer element (27) includes piston cap
(22)。
10. the hydraulic valve of the camshaft phase adjuster for camshaft, it includes housing (2) and can be along the housing (2)
The piston (4) of central opening (5) the axial direction activity of first longitudinal axis (3) extension, wherein the working joint of especially described housing (2)
The opening in place and closure of (A, B) according to the piston (4), and wherein described piston (4) is in order to avoid the piston that flows
(4) hydraulic fluid is associated with working joint (A, B) from what the inner space (9) of piston (4) undesirably flowed out to piston (4)
Percolation opening (29,30) and with check-valves (25,26), it is characterised in that the piston (4) according to claim 1 to 9 it
Constructed described in one.
11. hydraulic valve according to claim 10, it is characterised in that the supply joint (P) is arranged in tubular structure
End (11) place of housing (2).
12. the hydraulic valve according to claim 10 or 11, it is characterised in that there are the hydraulic valve (1) other connections to open
Mouth (46,47), to adjust the camshaft phase adjuster interlocked with center.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US201662307745P | 2016-03-14 | 2016-03-14 | |
| USUS62/307,745 | 2016-03-14 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN107191236A true CN107191236A (en) | 2017-09-22 |
| CN107191236B CN107191236B (en) | 2019-11-08 |
Family
ID=59870812
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201710119961.8A Expired - Fee Related CN107191236B (en) | 2016-03-14 | 2017-03-02 | The hydraulic valve of the piston of hydraulic valve for camshaft phase adjuster and the camshaft phase adjuster for camshaft |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN107191236B (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110173315A (en) * | 2018-02-21 | 2019-08-27 | 伊希欧1控股有限公司 | The hydraulic valve of rotary motor adjuster for camshaft |
| CN111434895A (en) * | 2019-01-15 | 2020-07-21 | 伊希欧1控股有限公司 | Sleeve of phase adjuster of camshaft and phase adjuster of camshaft |
| CN111980774A (en) * | 2019-05-23 | 2020-11-24 | 伊希欧1控股有限公司 | Hydraulic valve for a phase adjuster of a camshaft |
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| CN104912610A (en) * | 2014-03-13 | 2015-09-16 | 德国海利特有限公司 | Hydraulic valve for rotary motor adjuster of cam shaft |
| EP2977569A1 (en) * | 2014-07-25 | 2016-01-27 | Delphi Technologies, Inc. | Camshaft phaser |
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| US20090107433A1 (en) * | 2007-10-25 | 2009-04-30 | Denso Corporation | Valve timing controller |
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Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110173315A (en) * | 2018-02-21 | 2019-08-27 | 伊希欧1控股有限公司 | The hydraulic valve of rotary motor adjuster for camshaft |
| CN110173315B (en) * | 2018-02-21 | 2021-11-16 | 伊希欧1控股有限公司 | Hydraulic valve for a rotary motor adjuster of a camshaft |
| CN111434895A (en) * | 2019-01-15 | 2020-07-21 | 伊希欧1控股有限公司 | Sleeve of phase adjuster of camshaft and phase adjuster of camshaft |
| CN111434895B (en) * | 2019-01-15 | 2022-03-04 | 伊希欧1控股有限公司 | Sleeve of phase adjuster of camshaft and phase adjuster of camshaft |
| CN111980774A (en) * | 2019-05-23 | 2020-11-24 | 伊希欧1控股有限公司 | Hydraulic valve for a phase adjuster of a camshaft |
| CN111980774B (en) * | 2019-05-23 | 2022-04-26 | 伊希欧1控股有限公司 | Hydraulic valve for a phase adjuster of a camshaft |
Also Published As
| Publication number | Publication date |
|---|---|
| CN107191236B (en) | 2019-11-08 |
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