DE102017205676A1 - Camshaft adjuster and motor vehicle with a camshaft adjuster - Google Patents

Abstract

The invention relates to a camshaft adjuster (10) for adjusting a phase position of a first shaft relative to a second shaft according to the preamble of claim 1. In the stator (42), starting from the first pressure chamber (14), a first stator leading radially outward -Abströmkanal (58) and starting from the second pressure chamber (18) a radially outwardly leading second stator outflow channel (52) is formed. Further, in the housing (38) with the first pressure chamber (14) fluidly connected, radially outwardly leading first housing outflow channel (20) and with the second pressure chamber (18) fluidly connected, radially outwardly leading second housing outflow channel (24), wherein the first housing outflow channel (20) and the second housing outflow channel (24) are operatively connected to at least one control valve (22), by means of which the first housing outflow channel (20) and the second housing outflow channel (24), if necessary, at least partially open to a radial outflow of fluid from the first pressure chamber (14) through the first stator outflow channel (58) and the first housing outflow channel (24) or from the second pressure chamber (18) to be able to effect the second stator outflow channel (52) and the second housing outflow channel (24).

Description

The invention relates to a camshaft adjuster for adjusting a phase position of a first shaft of an internal combustion engine relative to a second shaft, in particular according to the preamble of claim 1. Such a camshaft adjuster is used in particular for adjusting the phase position of a camshaft relative to a crankshaft or for adjusting the phase position of a first Camshaft opposite a second camshaft. The invention also relates to a motor vehicle with a camshaft adjuster.

Out DE 10 2011 013 046 A1 is a camshaft adjuster for adjusting a phase angle of a camshaft of an internal combustion engine relative to a camshaft rotationally driving crankshaft of this internal combustion engine known, the structure is particularly described on the outside of the rotor only partially and whose feasibility is likely to be questionable.

Out JP 09280020 A is a known as a valve timing controller hydraulically actuated camshaft actuator with an impeller designated as a rotor with a plurality of wings and a radially outer side surrounding the impeller housing with chambers forming, radially inwardly projecting chamber wall elements known. The impeller may be moved by varying the fluid pressure with a control valve disposed outside the housing and the inflow of fluid into the chambers in the radial direction as viewed from outside to inside. The outflow takes place in the radial direction from the inside to the outside. The control of the impeller is via the amount of inflowing fluid to one of the chambers.

The invention has for its object to provide a camshaft adjuster with rotor and stator and a motor vehicle with such a camshaft adjuster, with which a fast and efficient adjustment of the phase angle is possible.

The object is achieved according to the invention with the features of the independent claims. Further practical embodiments and advantages of the invention are described in connection with the dependent claims.

An inventive camshaft adjuster for adjusting a phase angle of a first shaft of an internal combustion engine relative to a second shaft has a surrounding of a stator impeller (also called rotor) with at least one wing, wherein the stator has at least one stop element for the impeller, so that the impeller is rotatably arranged in the stator over a certain angular range such that it separates a first pressure chamber from a second pressure chamber insofar as by rotating the impeller due to a changing relative position of the at least one blade to the stator, the volume of the first pressure chamber and the second pressure chamber changes in opposite directions. Both the impeller and the stator are rotatably disposed in a housing, one of which is operatively coupled to a first shaft (e.g., a crankshaft) and the other of these elements is operatively coupled to a second shaft (e.g., a camshaft). For supplying fluid into the first pressure chamber, at least one first inflow channel and for supplying fluid into the second pressure chamber, at least one second inflow channel is provided, wherein the first inflow channel opens into the first pressure chamber radially on the inside and wherein the second inflow channel radially into the second Pressure chamber opens. In the stator are - starting from the first pressure chamber - a first radially outwardly leading stator discharge channel and - starting from the second pressure chamber - a second radially outwardly leading stator discharge channel formed. Furthermore, in the housing a fluidically connected to the first pressure chamber, radially outwardly leading first housing discharge channel and a fluidically connected to the second pressure chamber radially outwardly leading second housing outflow channel is formed. The first housing outflow channel and the second housing outflow channel are functionally connected to at least one control valve, by means of which the first housing outflow channel and the second housing outflow channel can be at least partially opened, if necessary, to a radial outflow of fluid from the first pressure chamber to be able to effect through the first stator outflow channel and the first housing outflow channel or from the second pressure chamber through the second stator outflow channel and the second housing outflow channel.

An advantage of the camshaft adjuster according to the invention is that this allows rapid phase adjustment by the position by the outflow of fluid from the first pressure chamber or the second pressure chamber by means of the at least one control valve is controllable. This can be effected in particular by applying the same base pressure to the first pressure chamber and the second pressure chamber via the first inflow channel and via the second inflow channel. For this purpose, the first pressure chamber and the second pressure chamber can be connected to a shared pressure source. The pressure provided by the pressure source can also vary in this case, for example as a function of the rotational speed of an internal combustion engine. If a housing outflow channel is opened by means of the control valve (eg the first housing). Outflow channel), fluid flows out of the pressure chamber fluidically connected to this housing outflow channel (eg from the first pressure chamber) via the corresponding stator outflow channel (eg the first stator outflow channel) and the corresponding housing outflow channel (eg the first housing outflow channel). from. The pressure in the pressure chamber, from which fluid flows, is consequently reduced. Thereby, a rotation of the impeller is effected such that the volume of the pressure chamber is reduced with the reduced pressure. By the rotation of the impeller relative to the stator, the phase angle of the first shaft is adjusted to the second shaft. The pressure chamber, from which no fluid can flow, is permanently exposed to the base pressure from the corresponding inflow channel. As a result, the volume of this pressure chamber is increased, while the volume of the pressure chamber, from which fluid flows, decreases to the same extent and thus in opposite directions. The relative rotation of the impeller to stator can be terminated by the fact that by means of the control valve, the housing outflow channels are closed again and has set in the different pressure chambers again the same pressure. The impeller is then hydraulically clamped. The relative rotation can also be terminated by the fact that the impeller is rotated relative to the stator up to an end position in which the at least one wing comes into contact with a stop element of the stator.

The outflow of fluid in the radial direction outward is accelerated in the camshaft adjuster according to the invention by utilizing the centrifugal force insofar as the first housing outflow channel and the second housing outflow channel are formed radially outwardly oriented. As a result, with increasing rotational speed of the impeller, the centrifugal forces acting on the fluid and directed radially outwards increase, thus providing additional acceleration of the outflowing fluid.

The control valve of a camshaft adjuster according to the invention can take - in a particularly simple and practical embodiment - exactly three positions.

In a first position, the first housing outflow channel and the second housing outflow channel are closed so that fluid can not flow out of either the first pressure chamber or the second pressure chamber. The volume of the first pressure chamber and the second pressure chamber is in this case the same size when both pressure chambers are subjected to the same pressure and this pressure is present in both pressure chambers.

In a second position, the first housing outflow channel is at least partially opened by means of the control valve. Due to the different pressure conditions (overpressure in the first pressure chamber), fluid then flows from the first pressure chamber through the first stator outflow channel into the first housing outflow channel via the first stator outflow channel. The pressure in the first pressure space thereby decreases, while the pressure in the second pressure space is maintained. Accordingly, the impeller rotates relative to the stator such that the volume of the first pressure chamber decreases and increases the volume of the second pressure chamber.

In a third position of the control valve, the first housing outflow channel is closed, and the second housing outflow channel is at least partially open. In this case, fluid flows from the second pressure chamber via the second stator outflow channel into the second housing outflow channel. Accordingly, the impeller rotates relative to the stator such that the volume of the second pressure space decreases and the volume of the first pressure space increases.

Preferably, the first inflow channel, the second inflow channel, the first stator outflow channel, the second stator outflow channel, the first housing outflow channel and / or the second housing outflow channel are aligned in a predominantly radial direction, so that fluid with efficient use of the centrifugal force of in the housing rotating impeller and stator can flow into the pressure chambers and can flow out of the pressure chambers, particularly preferably, the said channels are all or partially oriented in the purely radial direction. As a result of the radial orientation, the pressure in the chambers, from which fluid can flow out, decreases rapidly, as a result of which the response of the impeller of a camshaft adjuster according to the invention improves and a rapid adjustment of the phase position between the first shaft and the second shaft is made possible.

The (in particular exclusively) radially oriented stator outflow passages may be formed as bores or through openings formed differently within the stator, in particular in a closed stator ring of a stator. In a stator with a closed stator ring, the stator ring can in particular form an outside contour with a circular cross-section, which can be used as a sliding bearing surface for a rotating movement in a housing.

The (in particular only) radially oriented housing outflow channels can be formed simply and inexpensively as bores or differently shaped through openings within the housing, in particular in such a way that the housing outflow channels directly adjoin adjacent stator Abströmkanäle adjacent so that no additional connecting sections or connecting lines are required.

In camshaft adjusters according to the invention, the control valve can be arranged radially on the outside of the stator. This enables a mechanically simple design, in particular in comparison to solutions known from the prior art with valves arranged on the inside of an impeller (for example so-called central valves) which have to be adapted to an inside contour of the impeller, the first shaft or the second shaft.

For the purposes of this disclosure, the term "fluid" means all in particular incompressible fluids, preferably oil including hydraulic oil. The camshaft adjuster according to the invention can in particular be operated with oil from an oil circuit provided for an internal combustion engine and supplied together with other oil circuits of a motor vehicle, for example with the pump of an oil circuit for lubricating and / or cooling an internal combustion engine.

In a practical embodiment, a plurality of first pressure chambers and a plurality of second pressure chambers are alternately arranged between the impeller and the stator, wherein the first pressure chambers via a in the circumferential direction of the first pressure chambers and radially outside of the stator extending first connecting channel and the second pressure chambers via a extending in the circumferential direction - and in particular axially spaced from the first connection channel - second connecting channel are fluid-conductively connected to each other. In this case, the first connection channel and the second connection channel preferably extend in each case over the entire circumference, in particular in a region between the housing and the stator, only in a stator ring or only in a housing surrounding the stator.

A plurality of pressure chambers distributed over the circumference have the advantage that a pressure distribution which is advantageous for a uniform drive results on the impeller, in particular if a respective vane is formed on the impeller for each pair of corresponding pressure chambers. In order to keep the pressure in all belonging to a group pressure chambers always at the same level, adjacent corresponding pressure chambers are preferably fluidly connected directly by means of a connecting channel.

In order to achieve such a fluidic connection, which is structurally simple to implement, in particular the first connecting channel and / or the second connecting channel may be formed as a control groove on an outer circumference of the stator and / or on an inner circumference of the housing. If in each case a control groove is provided as the first connection channel and as the second connection channel, these control grooves can preferably be formed axially spaced from one another (preferably parallel) on the outer circumference of the stator ring and / or on the inner circumference of the housing.

In order to effectively and efficiently seal the control grooves against each other and against the environment, they can each be limited in the axial direction by at least one sealing ring. In particular, control grooves can be formed by three sealing rings arranged axially spaced from one another, which are arranged (preferably parallel to one another) in a sealing manner between the outer circumference of a stator ring and the inner circumference of the housing.

In a further practical embodiment, the first inflow channel and the first stator outflow channel are arranged in a region of the first pressure chamber which faces the stop element, and / or the second inflow channel and the second stator outflow channel are arranged in a region of the second pressure chamber. which faces the stop element. In other words, the inflow channels and the stator outflow channels - as viewed in the circumferential direction - each arranged as possible in the outer half of the corresponding pressure chamber, in particular the outside immediately adjacent to the stop element, so that the respective inflow channel and stator outflow even at a Allow minimal removal of the impeller to the stop element a low-resistance inflow and outflow of fluid in the radial direction (without transverse flow in the circumferential direction through gaps between impeller and stator).

The first inflow channel and the second inflow channel may extend in particular in the radial direction (preferably in the purely radial direction) starting from a feed channel (preferably oriented in the axial direction) to the corresponding first pressure chamber or second pressure chamber. With regard to a uniform pressure supply and due to a structurally simple design, it is preferred if only one feed channel (central channel) is provided to direct fluid via the first inflow channel to a first pressure chamber (or more first pressure chambers) and to fluid via the second inflow channel a second pressure chamber (or more second pressure chambers) to conduct. A particularly good space utilization results when such a supply channel at least partially in one Connecting element is formed, in particular in a predominantly or exclusively axially extending direction. In particular, such connecting elements are suitable, which establishes a connection between the first shaft and the impeller and / or produces a fluid connection from a fluid supply into an impeller. The connecting element can be a connecting element generating a clamping force, in order to non-positively and / or positively non-rotatably connect the impeller with the first shaft. In this case, the connecting element may for example be a central valve screw. However, such a clamping force can also be produced by means of another, separate element.

It may be advantageous to arrange a check valve in the first inflow channel and / or in the second inflow channel. Preferably, a check valve is arranged in the first inflow channel and in the second inflow channel. By means of such check valves can be prevented that due to pressure fluctuations in the pressure chambers fluid flows back from a pressure chamber in the respective inflow channel and thus a feedback could arise in a printing system. This is especially to be avoided if the printing system supplies even more fluid circuits.

In a further practical embodiment, the control valve is arranged in the housing itself. This arrangement requires little space and is inexpensive to produce, because no separate further outflow channels outside the housing are required. The control valve is also well accessible for assembly and maintenance in this case. It is also advantageous that the housing - at any point in its circumference - can be designed for the arrangement of an arbitrarily shaped control valve. This makes it possible to use a camshaft adjuster according to the invention in almost any motor vehicle, wherein as a control valve a - in its outer geometry almost arbitrarily shaped - inexpensive standard component can be used.

Downstream of the control valve, at least one return channel is formed, which establishes a fluid connection to an oil pan. In order to keep the design effort low, it is preferred if exactly one return channel is provided. Thus, a closed circuit (and thus disconnected from other circuits) or an open circuit (i.e., coupled with other circuits) can be created for the fluid. Preferably, a camshaft adjuster according to the invention is coupled to an oil circuit, which conducts the oil via the return channel to an oil pan and, starting from the oil pan, supplies the pressure chambers again.

The at least one return channel may in particular, at least partially, be integrally formed in the housing. In particular, the return channel as a bore or by molding and / or forming openings can be easily and inexpensively produced directly in the manufacture of the housing.

The invention also relates to a motor vehicle with a camshaft adjuster as described above, wherein the return passage extending from the control valve in installation position only horizontally and / or in the direction of gravity. The return passage thus does not extend higher in any direction in the direction of gravity than in the area of the control valve. Such a design of the return passage allows fluid to be returned to the sump without further work (which would be required to pump the fluid against gravity) and, advantageously, by utilizing gravity. Thus, an inventive camshaft adjuster is particularly energy-efficient.

For the sake of completeness, reference is once again made at this point explicitly to a method for operating a camshaft adjuster according to the invention as described above, according to which at least one first pressure space and at least one second pressure space are continuously subjected to a base pressure and the relative position is an impeller by actuation of an outflow side the first pressure chamber and the second pressure chamber arranged control valve is controlled by a first housing outflow channel or a second housing outflow channel are opened as needed.

• 1 eine Prinzipskizze eines erfindungsgemäßen Nockenwellenverstellers mit einer angeschlossenen Ölversorgung,
• 2 den erfindungsgemäßen Nockenwellenversteller aus 1 in einer perspektivischen Ansicht,
• 3 den Nockenwellenversteller aus 2 in einer Schnittdarstellung,
• 4 den Nockenwellenversteller gemäß 2 und 3 ohne Gehäuse in einer schematischen Ansicht gemäß Pfeil IV-IV,
• 5a den Nockenwellenversteller gemäß den 2 bis 4 in einer Schnittdarstellung gemäß Linie Va-Va aus 4,
• 5b den Nockenwellenversteller gemäß den 2 bis 4 in einer Schnittdarstellung gemäß Linie Vb-Vb aus 4,
• 6 eine vergrößerte Ansicht des mit VI gekennzeichneten Bereichs aus 5a in einer zweiten Ausführungsform eines erfindungsgemäßen Nockenwellenverstellers,
• 7 den Nockenwellenversteller gemäß 2 bis 5 in einer Schnittdarstellung gemäß Linie VII-VII aus 3, und
• 8 den Nockenwellenversteller gemäß 2 bis 5 und 7 in einer Schnittdarstellung gemäß Linie VIII-VIII aus 3.

Further practical embodiments of the invention are described below in conjunction with the drawings. Show it:

• 1 a schematic diagram of a camshaft adjuster according to the invention with a connected oil supply,
• 2 the camshaft adjuster according to the invention 1 in a perspective view,
• 3 the camshaft adjuster off 2 in a sectional view,
• 4 the camshaft adjuster according to 2 and 3 without housing in a schematic view according to arrow IV-IV,
• 5a the camshaft adjuster according to 2 to 4 in a sectional view along line Va-Va 4 .
• 5b the camshaft adjuster according to 2 to 4 in a sectional view along line Vb-Vb 4 .
• 6 an enlarged view of the area marked VI 5a in a second embodiment of a camshaft adjuster according to the invention,
• 7 the camshaft adjuster according to 2 to 5 in a sectional view according to line VII-VII from 3 , and
• 8th the camshaft adjuster according to 2 to 5 and 7 in a sectional view according to line VIII-VIII 3 ,

1 gives an overview of the operation of an embodiment of a camshaft adjuster according to the invention 10 , The camshaft adjuster 10 includes a first inflow channel 12 in a first pressure room 14 opens and a second inflow channel 16, which in a second pressure chamber 18 empties. Starting from the first pressure chamber 14, a first housing discharge channel leads 20 to a control valve 22 , Starting from the second pressure chamber 18 leads a second housing outflow channel 24 to the control valve 22.

The camshaft adjuster 10 is via a feed channel 26 supplied with oil, starting from an oil pan 28 by means of a pump 30 is encouraged. By means of a check valve 32 will be feedback towards the pump 30 avoided, and by means of a pressure accumulator 34 is counteracted larger pressure fluctuations.

Starting from the control valve 22 Fluid is transferred via a return channel 36 conveyed back to the oil pan 28, so that a total of a fluid circuit results.

As in 1 is shown schematically, the control valve shown 22 take three different positions.

In the shown (upper) position of the control valve 22 the second housing outflow channel 24 is opened, while the first housing outflow channel 20 closed is.

In a middle position of the control valve 22 are the first housing outflow channel 20 and the second housing outflow channel 24 both closed.

In another (lower) position of the control valve 22 the first housing outflow channel 20 is opened, while the second housing outflow channel 24 closed is.

In conjunction with the 2 to 8th will be discussed below on the structural design of the camshaft adjuster 10 itself.

2 shows the camshaft adjuster 10 with an outer housing 38 in a perspective side view. On the housing shape and in a synopsis with 3 It can be seen that in the housing partly also the control valve 22 is arranged to control the camshaft adjuster. In 3 is also evident that the control valve 22 firmly with the housing 38 is screwed. A screw 40 This screw connection can be seen in the section shown.

The internal structure of the camshaft adjuster 10 is among others in 3 recognizable, which is a sectional view through the housing 38 shows.

As in. 3 can be seen, the housing has 38 a circular cross-section area in which a stator 42 rotatable within the housing 38 is arranged. The stator 42 includes a closed stator ring 46 and four, radially from the stator ring 46 inwardly extending stop elements 48 , Furthermore, the stator comprises 42 a first cover member 66 and a second cover member 80 (cf 5a and 5b ), wherein the first cover element 66 , the stator ring 46 with the stop elements 48 and the second cover member 80 rotatably connected to a stator unit with each other. Within the stator ring 46 is an impeller 44 arranged. Both the impeller 44 as well as the stator 42 are rotatably arranged about the rotation axis D.

The impeller 44 has four wings 50 on, each with a wing 50 such between two stop elements 48 of the stator 42 is arranged, that in each case a first pressure space 14 and a second pressure room 18 are separated from each other. The first pressure chambers 14 and the second pressure chambers 18 are fluidly not connected to each other, ie, a direct overflow of fluid from a first pressure chamber 14 in a second pressure chamber 18 or vice versa is not possible. In the embodiment shown, this results in a first group with four first pressure chambers 14 and a second group with four second pressure chambers 18 ,

The impeller 44 can be, if appropriate, the pressure differences between the first pressure chambers 14 and the second pressure chambers 18 prevail, relative to the stator 42 rotate to the phase position between a first shaft, not shown, which is coupled to the impeller 44, and a second shaft, not shown, connected to the stator 42 is bound to vary. During such relative movement between the stator 42 and the impeller 44 the volume of the first pressure chambers changes 14 and the second pressure chambers 18 in opposite directions.

For supplying fluid into the second pressure chambers 18 are each oriented in the radial direction inflow channels 16 provided, the radially inside in the second pressure chambers 18 lead. These are in an inner ring inside the impeller 44 educated. In the embodiment shown, there are four second inflow channels 16 in the impeller 44 formed, each inflow channel 16 exactly in an associated second pressure chamber 18 leads.

In the stator ring 46 are each - starting from the second pressure chambers 18 - Radially oriented, leading to the outside second stator discharge channels 52 intended. As in 3 The second inflow channels are clearly visible 16 and the second stator outflow passages 52 viewed in the circumferential direction in a region of the second pressure chambers 18 arranged, which the respective stop element 48 is facing. The second inflow channels 16 Here are even directly to the stop element 48 formed adjacent.

The second pressure chambers 18 are also fluid-conducting over a circumferentially and radially between the stator ring 46 and the housing 38 extending second connecting channel 54 connected to each other. As in the following in connection with the 4 to 6 will be explained in more detail, is the second connection channel 54 as a second control groove 56 directly on the outer circumference of the stator ring 46 educated.

In the case 38 is - starting from the second, annular connecting channel 54 - The second housing-outflow channel extending radially outward 24 formed, which fluidly with the in the housing 38 arranged control valve 22 connected is.

Analogous to the four second inflow channels 16 are also four second inflow channels 12 formed in the impeller 44. These are in 3 not visible, since they are formed in the axial direction in another plane. Similarly, analogous to the second elements described above, first stator outflow channels 58 , a first, annularly formed connecting channel 60 and a first housing discharge channel 20 educated.

In 4 is a view on the stator ring 42 according to the arrow IV in 3 shown. As can be seen, are - axially spaced from each other - a first stator discharge channel 58 and a second stator outflow channel 52 formed, each radially out of the stator ring 46 escape.

The first stator outflow channel 58 opens into the first connection channel 60 in the form of the ring-shaped, first control groove 62 and the second stator outflow channel 52 opens into the second connection channel 54 in the form of the annular, second cam groove 56 (see also 5a and 5b ). The first connection channel 60 and the second connection channel 54 are axially spaced and parallel to each other on the outer periphery of the stator ring 46 educated.

In 5a is a cross section through the housing 38 according to the line Va-Va in 4 shown. This section passes through a second pressure chamber 18 ,

In this sectional view, a connecting element 64 arranged in the region of the axis of rotation D in the form of a central valve screw is provided for non-rotatable connection of the impeller 44 and for coupling the impeller 44 over the connecting element 64 with a first wave (not shown) recognizable. At the connecting element 64 is a central supply channel 26 formed in the axial direction from the left side in the connecting element 64 extends into it. About the feed channel 26 will fluid from the sump (in 5a not shown) to the first inflow channel 12 (see. 5b ) and to the second inflow channel 16 directed. To the fluid to the first inflow channel 12 or to the second inflow channel 16 to lead, extends the feed channel 26 within the connecting element 64, starting from the axially formed section and also at a first location in the radial direction up to the first inflow channel 12 and at a second location to the second inflow channel 16 ,

As in 5a is recognizable extending - starting from the second pressure chamber 18 - In the purely radial direction of the second stator discharge channel 52 and the second housing discharge passage 24.

In 5a is also good to see that the stator 42 from the stator ring 46 , which in the axial direction on both sides of the first cover element 66 and the second lid elements 80 is enclosed and rotatably connected with these, is formed.

On an outer peripheral portion of the first lid member 66 is a gear structure 68 trained to the stator 42 with a second wave (not shown) to be able to couple.

In 5a It is good to see that the second connection channel 54 as a second control groove 56 and the first connection channel 60 as first rudder 62 are formed on the outer periphery of the stator ring 46. Axially adjacent to the first control groove 62 and the second control groove 56 are respectively seals 70 arranged. With the sealing rings 70 ensures that no fluid from the with the first control groove 62 fluid-conducting coupled first pressure chambers in the second control groove 56 or in the with the second control groove 56 fluid-conducting coupled second pressure chambers 18 arrives. Likewise with the sealing rings 70 prevents fluid differently than via the stator outflow channels 52 . 56 from the first pressure chambers 14 or from the second pressure chambers 18 gets out into the environment.

5b shows a section along the line Vb-Vb in 4 , This section runs through a first pressure chamber 14 , In this sectional view, the first (here exclusively) radially extending inflow channel 12 to recognize the (here exclusively) radially extending first stator outflow channel 58 and the (here exclusively) radially extending first housing outflow channel 20. The other elements are identical to those in 5a shown elements.

In 6 is a detailed representation of a second inflow channel 16 with its mouth in a second pressure chamber 18 shown. As can be seen, the second inflow channel 16 a check valve 72 is arranged, which is a ball 74 and a retaining ring 76 includes. The check valve 72 is designed so that it is at overpressure in the inflow 26 opens until the pressure in the inflow channel 26 also in the second pressure chamber 18 prevails. At a possible overpressure in the second pressure chamber 18 closes the check valve 72 and allows a backflow of fluid from the second pressure chamber in the second inflow channel 16 and the feed channel 26 not too.

Such a check valve 72 is in all second inflow channels 16 provided that a plurality of inflow channels are provided. It is at least one inflow channel 16 intended. Also, such a check valve 72 - In an analogous manner - also provided in all the first inflow channels 12, which are the first pressure chambers 14 lead, if several inflow channels 12 are provided. It is at least a first inflow channel 12 intended.

With the help of a synopsis of the 7 and 8th will now be the return of the fluid from the camshaft adjuster 10 in the direction of the oil pan 28 explained. Starting from the control valve 22 extends a return channel 36 immediately inside the housing 38 first in a purely horizontal orientation, ie perpendicular to gravity g, and then in the direction of gravity g. The return channel 36 is designed as a bore within the housing 38. Not provided for guiding fluid portions of the holes are with balls 78 locked. How out 8th As can be seen, the return channel 36 also extends partially into a region of the housing 38 , which serves to receive the stator 42. The return channel 36 extends in mounting position only horizontally or with a component in the direction of gravity g.

Furthermore, in 8th still the gear 68 for coupling with the second shaft and a part of the axially projecting connecting element 64 to recognize.

The following is the operation of the camshaft adjuster 10 and the method for operating the camshaft adjuster 10 explained again with reference to the figures:

Starting from the feed channel 26 Fluid is always through the first inflow channels 12 in the first pressure chambers 14 passed and via the second inflow channels 16 directed into the second pressure chambers 18 when the fluid pressure in the first pressure chambers 14 or in the second pressure chambers 18 is lower than in the feed channel 26 , In other words, the first pressure chambers become 14 and the second pressure chambers 18 basically subjected to the same pressure, so that the impeller 44 when the control valve is closed 22 is hydraulically clamped and facing the stator 42 not moved relatively.

In the in 3 shown position, there is the impeller 44 relative to the stator 42 in a middle position, in which between the wings 50 and the respective outside adjacent stop elements 48 first pressure chambers 14 and second pressure chambers 18 each formed with the same volume. Due to the closed position of the control valve 22 can not fluid from the first pressure chambers 14 or the second pressure chambers 18 flow.

Will the position of the control valve 22 changed, for example, such that the second housing outflow channel 24 is opened, fluid from the second pressure chambers 18 respectively through the second stator outflow channels 52 in the second connection channel 54 arrive and from the second connection channel 54 in the second housing outflow channel 24 , This reduces the pressure in the second pressure chambers 18 opposite the pressure in the first pressure chambers 14, which causes the impeller 44 relative to the stator 42 twisted so that the volume of the second pressure chambers 18 reduces and contrasts the volume of the first pressure chambers 14 elevated. This adjusts the phase position of the first shaft relative to the second shaft. The impeller 44 can only turn as far as the stator 42 until the wings 50 at the stop elements 48 attacks.

To the impeller 44 relative to the stator 42 to turn in the opposite direction, the second housing discharge channel 24 from the control valve 22 closed and the first housing-discharge channel 20 is opened by the control valve is moved to the appropriate position.

The inflow of fluid through the first inflow channel 12 and the second inflow channel 16 and the outflow of fluid through the first stator outflow passage and the first housing outflow passage or the second stator outflow passage 52 and the second housing-outflow channel 24 takes place in each case purely radially, so that the centrifugal force of the rotating impeller 44 and the rotating stator 42 is exploited to increase the outflow velocity of the fluid and thus to improve the response time of the camshaft actuator according to the invention.

The features of the invention disclosed in the present description, in the drawings and in the claims may be essential both individually and in any desired combinations for the realization of the invention in its various embodiments. The invention may be varied within the scope of the claims and in consideration of the knowledge of the person skilled in the art.

LIST OF REFERENCE NUMBERS

10

Phaser

12

first inflow channel

14

first pressure chamber

16

second inflow channel

18

second pressure chamber

20

first housing outflow channel

22

control valve

24

second housing outflow channel

26

feed

28

oil pan

30

pump

32

check valve

34

accumulator

36

Return channel

38

casing

40

screw

42

stator

44

impeller

46

stator

48

stop element

50

wing

52

second stator outflow channel

54

second connection channel

56

second control groove

58

first stator outflow channel

60

first connection channel

62

first rudder

64

connecting member

66

first cover element

68

gear

70

seal

72

check valve

74

Bullet

76

Retaining ring

78

Bullet

80

second cover element

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• DE 102011013046 A1 [0002]
• JP 09280020 A [0003]

Claims (10)

Camshaft adjuster for adjusting a phase angle of a first shaft of an internal combustion engine relative to a second shaft, with one of a stator (42) surrounded impeller (44) having at least one wing (50), wherein the stator (42) at least one stop element (48 ) for the impeller (44), so that the impeller (44) is rotatably arranged in the stator (42) over a certain angular range such that it separates a first pressure chamber (14) from a second pressure chamber (18) insofar The volume of the first pressure chamber (14) and of the second pressure chamber (18) changes in opposite directions by a rotation of the impeller (44) due to a changing relative position of the at least one blade (50) to the stator (42), wherein the impeller (44 ) and the stator (42) in a housing (38) are arranged, wherein at least a first inflow channel (12) for supplying fluid into the first pressure chamber (14) and at least a second Z. The first inflow channel (12) opens radially into the first pressure chamber (14) and the second inflow channel (16) projects radially inward into the second pressure chamber (FIG. 18), characterized in that in the stator (42) starting from the first pressure chamber (14) a radially outwardly leading first stator outflow channel (58) and starting from the second pressure chamber (18) a radially outwardly leading second stator -Abströmkanal (52) are formed, and in that in the housing (38) with the first pressure chamber (14) fluidly connected, radially outwardly leading first housing outflow channel (20) and with the second pressure chamber (18) fluidly connected, radially outwardly leading second housing outflow channel (24) are formed, wherein the first housing outflow channel (20) and the second housing outflow channel (24) functionally connected to at least one control valve (22) By means of which the first housing outflow channel (20) and the second housing outflow channel (24) can be at least partially opened, if necessary, in order to allow a radial outflow of fluid from the first pressure chamber (14) through the first stator outflow channel (58 ) and the first housing-outflow channel (24) or from the second pressure chamber (18) through the second stator outflow channel (52) and the second housing outflow channel (24) to be able to effect. Camshaft adjuster according to the preceding claim, characterized in that between the impeller (44) and the stator (42) a plurality of first pressure chambers (14) and a plurality of second pressure chambers (18) are each arranged alternately, wherein the first pressure chambers (14) via a in the circumferential direction extending first connecting channel (60) and the second pressure chambers (18) via a circumferentially extending second connecting channel (54) are fluid-conductively connected to each other. Camshaft adjuster according to the preceding claim, characterized in that the first connecting channel (60) and / or the second connecting channel (54) as a control groove (62, 56) on an outer circumference of the stator (42) and / or on an inner circumference of the housing (38 ) are formed. Camshaft adjuster according to the preceding claim, characterized in that the control grooves (56, 62) each viewed in the axial direction of at least one sealing ring (70) are limited. Camshaft adjuster according to one of the preceding claims, characterized in that the first inflow channel (12) and the first stator outflow channel (58) in a region of the first pressure chamber (14) and / or the second inflow channel (16) and the second stator outflow channel (52) are arranged in a region of the second pressure chamber (18) which faces the stop element (48). Camshaft adjuster according to one of the preceding claims, characterized in that the first inflow channel (12) and the second inflow channel (16) are fluidly connected to a feed channel (26), wherein the feed channel (26) at least partially in a connecting element (64) of the first Shaft is formed extending in the axial direction and / or in the radial direction of the connecting element (64). Camshaft adjuster according to one of the preceding claims, characterized in that the control valve (22) in the housing (38) is arranged. Camshaft adjuster according to one of the preceding claims, characterized in that starting from the control valve (22) at least one return channel (36) is formed, which establishes a fluid connection to an oil sump (28). Camshaft adjuster according to the preceding claim, characterized in that the return channel (36) is formed at least partially in one piece in the housing (38). Motor vehicle with a camshaft adjuster (10) according to one of the two preceding claims, characterized in that extending from the control valve (22) in the installation position only horizontally and / or in the direction of gravity of the return channel (36).

Images