KR101239610B1 - Sealing element for sealing an axial end of a control valve and control valve - Google Patents

Abstract

The present invention relates to a control valve 101 for controlling a hydraulic device 1 for changing a control time of a gas exchange valve of an internal combustion engine. According to the invention, the control valve 101 is housed in the valve receiving portion 106, and an elastic sealing member 124 is provided at the axial end of the control valve 101. By using the resilient closure member 124, the leakage flow between the pressure medium channels 113 and between these pressure medium channels 113 and the discharge connection T is suppressed in a manner which ensures a reliable function. . Also proposed is an elastic sealing member 124 having two conical regions 129 and 131 configured as a sealing ring.

Gas exchange valve, hydraulic device, control valve, elastic sealing member.

Description

SEALING ELEMENT FOR SEALING AN AXIAL END OF A CONTROL VALVE AND CONTROL VALVE

The present invention relates to a sealing member according to the preamble of claim 1 and a control valve for controlling the supply and discharge of a pressure medium to a device for changing the control time of an internal combustion engine according to the preamble of patent claim 4. will be.

In the case of internal combustion engines, camshafts are used to operate gas exchange valves. The camshafts are mounted to the internal combustion engine in such a way that the cams mounted thereon are adjacent to cam followers, such as bucket type tappets, finger rocker arms or finger type rockers. When the camshaft rotates, the cams roll on the cam followers, which in turn activate the gas exchange valves. Therefore, by the position and shape of the cams, the opening amplitude as well as the opening amplitude and opening and closing timings of the gas exchange valves are determined.

The modern engine design consists in designing the valve timing gear in a variable manner. The valve head and the valve opening period can be implemented variably until the individual cylinders on one side are completely deactivated. To this end, a design is provided, such as a shiftable cam follower, an electrohydraulic valve actuating device, or an electric valve actuating device. It has also been found to be desirable to be able to influence the opening and closing times of gas exchange valves during operation of the internal combustion engine. In this regard, it is particularly desirable to independently influence the opening and closing points of the intake valves and the exhaust valves, for example in order to adjust the defined valve overlap. Depending on the actual performance characteristic area of the engine, for example, depending on the actual rotational speed or the actual load, by adjusting the opening or closing timing of the gas exchange valves, the fuel consumption rate can be reduced, which can have a positive effect on the exhaust gas behavior. And the engine efficiency, maximum torque, and maximum power can rise.

The aforementioned variability in gas exchange valve control time is achieved by changing the phase position of the camshaft relative to the crankshaft. In this connection, the camshaft is usually driven in connection with the crankshaft by means of a chain drive, belt drive, toothed gear drive, or a drive design with the same effect. Between the chain, belt or toothed gear drive driven by the crankshaft and the camshaft, a device for changing the control time of the internal combustion engine (hereinafter also referred to as camshaft adjusting device) is mounted, and this changer is the torque of the crankshaft. To the camshaft. In this regard, the change device is such that the phase position between the crankshaft and the camshaft remains fixed while the internal combustion engine is in operation, and, if desired, in such a way that the camshaft can be rotated against the crankshaft in a predetermined angle region. Is composed.

In the case of an internal combustion engine having respective camshafts for intake valves and exhaust valves, the camshafts may have respective camshaft adjusting devices. By doing so, the opening and closing timings of the intake and exhaust gas exchange valves are relatively temporarily displaced from each other, and the valve overlap can also be adjusted as desired.

The seating portion of a modern camshaft adjustment device is usually located at the drive side end of the camshaft. However, the camshaft adjusting device may be arranged on the intermediate shaft, the non-rotating structural member or the crankshaft. The camshaft adjusting device includes a drive wheel that is driven by the crankshaft and maintains a fixed phase relationship to the crankshaft, a driven member connected to the camshaft and an adjusting mechanism that transmits torque of the drive wheel to the driven member. . The drive wheel can be configured as a chain sprocket, belt pulley, or toothed gear when the camshaft adjuster is not placed on the crankshaft, and driven by the crankshaft using a chain drive, belt drive or toothed gear drive. do. The adjustment mechanism can be driven electrically, hydraulically or pneumatically.

Two preferred embodiments of the hydraulically adjustable camshaft adjusting device are the so-called axial piston adjusting device and the rotary piston adjusting device.

In the case of an axial piston adjustment device, the drive wheel is connected with the piston via a helical gear, and the piston is also connected with the driven member via the helical gear. The piston separates the hollow chamber formed by the driven member and the drive wheel into two pressure chambers disposed axially with each other. Thus, if one pressure chamber is supplied with a pressure medium, while the other pressure chamber is in communication with the tank, the piston is displaced axially. The axial displacement of the piston is converted through the helical gears to the relative rotation of the drive wheel relative to the driven member and thus the relative rotation of the camshaft with respect to the crankshaft.

The second embodiment of the hydraulic camshaft adjusting device is a so-called rotary piston adjusting device. In this case, the drive wheel is fastened in rotation with the stator. The stator and the rotor are arranged concentrically with each other, and the rotor is engaged with the camshaft, the extension of the camshaft, or the intermediate shaft, for example, by a frictional coupling method, a shape coupling method, or a material coupling method using a press fit, screw or weld joint. do. Within the stator are formed a plurality of hollow chambers spaced apart in the circumferential direction, which extend from the rotor and extend outward in the radial direction. The hollow chambers are confined in a high pressure sealed manner by side covers in the axial direction. Inside each of the hollow chambers extends a wing connected with the rotor. The wing separates each hollow chamber into two pressure chambers. By communicating the hydraulic pump or tank with the individual pressure chambers as desired, the phase of the camshaft relative to the crankshaft can be adjusted or fixed.

In order to control the camshaft adjusting device, the sensor detects characteristic data of the engine, such as load state and rotation speed. The data is supplied to the electronic control unit, which compares the supplied data with the characteristic map of the internal combustion engine and then calculates the set value of the relative phase angle between the camshaft and the crankshaft. Via a sensor, for example a hall sensor, the actual value of the phase angle and the deviation of the actual value with respect to the set value are measured. Subsequently, control commands are directed to the control unit of the control valve, which controls the supply and discharge of the pressure medium to the various pressure chambers and thus the adjustment of the phase position of the camshaft.

In the hydraulic camshaft adjusting device, in order to adjust the phase position of the camshaft against the crankshaft, in the hydraulic camshaft adjusting device, the pressure chamber on one side of the two interacting pressure chambers of the hollow chamber is in communication with the hydraulic pump, and the pressure chamber on the other side of the tank In communication with The supply of the pressure medium consisting of one chamber in conjunction with the discharge of the pressure medium from the other chamber causes an axial displacement of the piston separating the pressure chambers, so that in the axial piston adjustment device the camshaft is cranked through the helical gears. Rotated relative to the axis. In the case of the rotary piston adjusting device, pressure is applied to the chamber on one side, and pressure is reduced on the chamber on the other side to cause displacement of the wing, thereby directly causing rotation of the cam shaft about the crankshaft. To fix the phase position, the two pressure chambers are in communication with the hydraulic pump or separated from the tank as well as the hydraulic pump.

Control of the pressure medium flow to the pressure chambers is done using a control valve, usually using a 4/3 proportioning valve. The valve housing has a respective connection (work connection) for the pressure chambers, a connection to the hydraulic pump, and at least one connection to the tank. Inside the valve housing, which consists essentially of a hollow cylinder, an axially displaceable control piston is arranged. The control piston is moved to a respective position between the two final positions defined in the axial direction against the spring force of the spring member, using a control unit, for example an electromagnetic or hydraulic control unit. The control piston also has an annular groove and a control edge, whereby the individual pressure chambers can alternatively be in communication with the hydraulic pump or in communication with the tank. Likewise, the position of the control piston where the pressure chambers are separated from the pressure medium tank as well as the hydraulic pump can be provided.

The control valves can be configured as a central valve or as a cartridge valve. In the case of being configured as a center valve, the center valve is disposed in the area of the camshaft adjusting device within the camshaft or inside the extension of the camshaft. When configured as a cartridge valve, the adjacent members of the internal combustion engine should have a valve compartment into which the corresponding control valve is inserted. Pressure medium lines are formed on the outer surface of the valve receiving portion, which is usually configured as a bore portion, and these pressure medium lines communicate with the pressure medium connections of the control valve. The adjacent member may for example be a cylinder head or a cylinder head cover.

DE 102 23 431 B4 discloses such a changeover device with a cartridge type control valve. The changing device thus consists of a driven unit fixed to the camshaft, a drive unit driven by the crankshaft and two side covers. The drive unit is arranged coaxially with respect to the driven unit and has a plurality of recesses spaced apart in the circumferential direction. These recesses are closed in a high pressure sealed manner by the drive unit, the driven unit and the side covers, thus forming pressure chambers. The wing extends into each pressure chamber and each wing is disposed in a wing groove formed in the driven unit. Each wing separates the pressure chamber into two interacting pressure chambers. The pressure chambers are in communication with further pressure medium lines arranged in the cylinder head or the cylinder head cover, using a rotating joint, via pressure medium lines arranged in the camshaft.

The additional pressure medium lines can be communicated alternately with the pressure medium reservoir or the hydraulic pump using a control valve, here a 4/3 directional control valve. The control valve consists of a control unit and a valve body. The valve body is surrounded by an adapter sleeve, which is disposed in the bore of the cylinder head cover. Within the adapter sleeve are provided three radial openings which are spaced apart from each other in the axial and circumferential directions. These radial openings are used as pressure medium connections. The fourth pressure medium connection is formed in the axial direction on the leading end face of the valve body that faces in the opposite direction of the control unit. Each radial opening communicates with the pressure medium line through each vertical channel. The pressure medium reaches a radial opening axially centrally through the pressure medium line, from which it enters the interior of the sleeve, the pressure medium flow being directed to one of the other two radial openings depending on the control position of the control valve. Guided to the radial opening. The pressure medium then reaches, via an additional vertical line, a pressure medium line in communication with the first pressure chamber group essentially with the rotary joint on one of the rotary joints.

In a similar manner, the pressure medium reaches an additional vertical line which is open to the third radial opening via the rotary joint and pressure medium lines from the second pressure chamber group. The pressure medium is then guided through the control valve to the axial discharge connection. The vertical lines are formed in the bore in the cylinder head cover and as grooves open towards the adapter sleeve. In addition, the outer diameter of the adapter sleeve is formed to match the inner diameter of the bore portion so that the vertical lines are closed against each other. The pressure medium lines in communication with the vertical lines are provided in the cylinder head cover according to the present embodiment and are formed as grooves open in the direction of the cylinder head. In order to enable the outflow of the pressure medium exiting the pressure chambers, the cylinder head has an outflow bore arranged coaxially with the bore formed in the cylinder head cover.

To avoid leakage between the vertical lines and the outlet bore, the inner diameters of the bore and outlet bore are the same, and the adapter sleeve extends at least partially into the adapter bore. The adapter sleeve is hermetically seated on the outer face of the outlet bore, whereby the outflow of pressure medium from the vertical lines into the cylinder head via the outlet bore is suppressed. Even if the bores are only slightly offset from each other, the adapter sleeve is damaged during assembly, which can lead to a loss of the sealing effect between the structural members.

In order to ensure a sealing function between the vertical channels and the outlet bore, the bore must be exactly coaxially aligned with the outlet bore and the adapter sleeve diameter must be exactly matched to the inner diameter of the outlet bore. This can only be achieved at very high costs, based on the inevitable tolerances in the manufacturing process of the individual structural members.

It is an object of the present invention to propose a hermetic design for a control valve which avoids the above mentioned disadvantages and overcomes the tolerances that occur in the system. Further, another object of the present invention is to propose a sealing member for use in the sealing design.

The control valve for controlling the supply and discharge of the pressure medium to the device for changing the control time of the internal combustion engine is, among other things, arranged essentially inside the valve housing and the valve housing in which the pressure medium connections are formed. And a control piston that is displaceable in the axial direction. In this regard, depending on the position of the control piston, it may be communicated or separated between different pressure medium connections. The valve housing is disposed in the valve housing, and the insertion depth in which the valve housing is mounted in the valve housing is limited by the axial stop formed in the valve housing. The object is that, according to the invention, the axial stop is formed as a wall of circular or circular ring shape, which wall starts from the inner surface of the valve compartment and extends in a radial direction inward, and the valve housing and the valve This is achieved by arranging the closure member between the axial stops of the enclosure.

The control valve is composed of a cylindrical valve housing and a control piston disposed axially displaceable within the valve housing. The valve housing has radial openings used as pressure medium connections. Using the control unit, the control piston can be moved to any position between the two end stops inside the valve housing. The control piston then communicates or disconnects several pressure medium connections depending on their relative position to the valve housing. The control piston can be in direct contact with the valve housing. In addition, as described in DE 102 23 431, a control sleeve can be provided which is arranged hollow between the valve housing and the control piston. The inner diameter of the control sleeve corresponds to the outer diameter of the control piston, and the outer diameter of the control sleeve corresponds to the inner diameter of the valve housing. The outer surface of the control sleeve also has a plurality of annular grooves, which communicate with the pressure medium connections on one side and on the other side with the inside of the control sleeve via radial openings. By axially displacing the control piston, communication or separation can be made between the annular grooves and thus between the pressure medium connections, and in some cases communication with the axial pressure medium connection can be realized or separated.

The control valve is disposed in the valve compartments, in which pressure medium channels are formed in communication with the pressure medium connections. Through the pressure medium channels, the pressure chambers of the camshaft adjustment device are in communication with the hydraulic pump or the pressure medium reservoir. The valve compartments may for example be formed in the cylinder head or in the cylinder head cover. This is usually called a cartridge valve. Moreover, a control valve can also be used as a center valve. In this case, the control valve is disposed in the valve housing in the camshaft, and rotates with the camshaft when the internal combustion engine is operated.

In both cases, the valve receiving portion is configured as a cylindrical bore portion. The outer diameter of the valve housing corresponds to the inner diameter of the bore, whereby the pressure medium connections are sealed against each other. Inside the bore part an axial stop for the valve housing is provided. The axial stop can be configured as a wall that limits the range of the bore. Similarly, the diameter of the bore is constricted. In this case the bore portion is formed in a stepped cross section, thereby forming a ring section which is used as an axial stop for the valve housing. Furthermore, a sealing ring is provided between the axial stop and the valve housing to suppress leakage flow in the axial direction.

In this way, the radial ring closure position described in DE 102 23 431 is moved axially, so that the influence of the tolerances associated with the dimensions of the control valve is not critical.

According to a preferred refinement of the invention, the axial stop side leading end of the valve housing is formed with an area of reduced outer diameter, and the sealing member is disposed at least partially in an area of reduced outer diameter. The sealing member is also configured as a sealing ring having an outer surface and an inner surface.

The area of reduced outer diameter facilitates the assembly of the sealing member and the control valve in the valve compartment. The inner diameter of the sealing member configured as the sealing ring corresponds to the outer diameter of the region where the outer diameter decreases. In this area the sealing ring is fitted on the control valve and positioned with the control valve in the valve compartment. Therefore, assembly defects are avoided on the basis of the guide and center determination taken on the sealing member using the control valve, and the sealing action is stably performed during the processing.

In addition, the sealing member may be composed of an elastomer. The sealing ring is seated at the end of the axial stop side at the outer surface of the region when the valve housing is provided with a region of decreasing outer diameter. The sealing ring is also extended in the axial direction by the valve housing and the axial stop. During assembly, the sealing ring is pressed against the axial stop by the valve housing. At this time, the sealing ring is elastically deformed, and deformation from the radial direction to the inner direction is suppressed by the valve housing. The elastic deformation thereby ensures a "preferred direction" towards the inner face of the valve compartment, that is to say from the radial direction to the outward direction. By doing so, the sealing action is increased or obviously achieved more quickly. A further advantage when using an elastic sealing ring is that the axial tolerance can be compensated for through the deformation of the sealing ring.

The elastomer may be for example fluororubber or acrylonitrile butadiene rubber. These materials have a very good resistance to very good properties against internal influences in internal combustion engines such as high temperatures and in contact with engine oil.

According to a further embodiment of the invention, the valve receiving portion consists of a first bore portion and a second bore portion, which bores are formed from different adjacent members, are arranged in at least a substantially coaxial manner with each other, and It is composed in the form of communication between the liver. For this embodiment, for example, the valve compartment described in DE 102 23 431 can be mentioned. Each bore is provided in the cylinder head and the cylinder head cover. The two bores are arranged in a manner that is at least nearly coaxial with one another when the cylinder head cover is assembled on the cylinder head.

According to an improved embodiment of the invention, the axial stop can be formed at the interface of two adjacent members. In this embodiment, the inner diameter of the second bore portion is configured to be smaller than the inner diameter of the first bore portion. In other words, a step is formed at the interface between the two bores. The advantage of this variant is the low manufacturing cost, since the stepped portion is realized by arranging two bores with different inner diameters in succession.

According to an alternative method, the axial stop is formed in a second bore portion second in the insertion direction of the control valve. The advantage here is that the stepped extension of the bore portion can be constructed in such a way that the sealing member can be seated on the inner surfaces of the bore portions at the interface of the two adjacent members.

In this embodiment according to the present invention, since the outer surface of the valve housing no longer functions as a sealing function at the interface of the adjacent members, the inner diameter of the second bore portion is larger than the inner diameter of the first bore portion at the interface between the adjacent members. And, accordingly, larger than the outer diameter of the valve housing. Therefore, even if the bores are slightly offset from each other, the control valve can be safely assembled without breaking the control valve.

In addition, the axial stop is disposed and the closure member is formed in such a way that the closure member rests on the boundary of the two adjacent members in the valve receiving portion. Therefore, leakage paths, which are sometimes caused by edges that are not at right angles, are blocked in a reliable manner by the elastic deformation of the closure member.

According to a preferred refinement of the invention, the diverting region of the valve housing which is diverted to the region of decreasing diameter is at least partially conical. The closure member also has a first conical region on its own inner surface, which corresponds to the diverting region of the valve housing.

The valve housing consists of first and second cylindrical regions. The first cylindrical region is hermetically seated in the inner wall of the first bore portion. The second area is an area in which the outer diameter decreases. A conical transition region is formed in the transition portion that is switched from the first region to the second region. In this regard, the overall diameter reduction can be connected using a conical region. Similarly, starting from the first region, it is also conceivable that the valve housing extends radially inwardly in a staircase shape before switching to a conical region in which the outer diameter reducing region is initiated. The closure ring is arranged in such a transition region, the contour of the closure ring seated in the valve housing conforms to the contour of the valve housing, in particular to the contour of the conical region. While assembling the control valve to the valve compartment, the valve housing applies a load to the seal ring. On the basis of the fact that the pressure surface extends not parallel to the axial stop, the sealing ring is loaded in the radial direction as well as in the axial direction. As a result, further improved sealing action is achieved in the radial direction.

According to a preferred refinement of the invention, the outer surface of the closure member has a second conical region at the tip that rests on the axial stop, thereby creating a ring-shaped hollow chamber between the closure member and the axial stop. do. For example, if a larger axial tolerance is to be compensated and the valve must be positioned within the valve compartment, the sealing ring can be deflected into the hollow chamber while maintaining its own sealing function. Larger manufacturing tolerances can be compensated for, resulting in lower costs.

The sealing member is also proposed in the form of a sealing ring having an inner surface and an outer surface for sealing the axial leading end of the control valve of the device for changing the control time of the gas exchange valves. The object according to the invention is achieved by the inner face and the outer face having conical regions on each of their annular edges. In this connection two conical regions are formed in their annular edges which are axially offset from one another in the sealing ring. The region on one side of these conical regions is provided for seating in the conical region of the structural member where the sealing ring should be closed against the second structural member. In this connection, in particular the structural member is hermetically assembled inside the bore, and the sealing ring is subjected to an axially directed load. The conical crimping surface of the structural member thus converts its axial load into radial and axial load components, whereby the sealing ring deforms in the radial direction, thereby increasing the sealing action. By forming another annular edge in a conical shape, a ring shaped hollow chamber is provided, wherein the sealing ring can be deflected into the hollow chamber under the action of a load. As such, through such hollow chambers, large axial tolerances can be compensated for without compromising the sealing action.

Further features of the invention are presented from the following description of the embodiments and of the drawings in which embodiments of the invention are shown in outline.

Fig. 1 is a longitudinal sectional view showing a cutout apparatus for changing the control time of an internal combustion engine having a hydraulic circuit.

FIG. 2 is a cross-sectional view showing the device shown in FIG. 1 by cutting along the cut line II-II.

Fig. 3 is a longitudinal sectional view of the control valve assembled to the valve receiving section according to the first hermetic design of the present invention.

FIG. 4 is a cross-sectional view of the control valve shown in FIG. 3 cut along the cut line IV-IV.

Fig. 5 is a longitudinal sectional view of the control valve assembled to the valve receiving section according to the second hermetic design of the present invention.

FIG. 6 is a cross-sectional view of the control valve shown in FIG. 5 cut along the cut line VI-VI.

Figure 7 is a longitudinal sectional view showing the sealing ring in accordance with the present invention.

FIG. 8 is a cross-sectional view showing the sealing ring shown in FIG. 7 by cutting along the cut lines VIII-VIII.

1 and 2 show an apparatus 1 for changing the control time of an internal combustion engine. The changing device 1 consists essentially of the stator 2 and the rotor 3 arranged concentrically therewith. The drive wheel 4 is fastened rotatably with the stator 2, and is formed as a chain sprocket in the illustrated embodiment. Similarly, it is conceivable to design the drive wheel 4 as a belt pulley or a toothed gear. The stator 2 is rotatably mounted on the rotor 3, and the inner surface of the stator 2 is provided with five recesses 5 spaced apart in the circumferential direction according to the illustrated embodiment. These recesses 5 are provided by the stator 2 and the rotor 3 in the radial direction, by the two side wall portions 6 of the stator 2 in the circumferential direction, and by the first and second in the axial direction. The range is defined by the side cover parts 7 and 8. Each recess 5 is closed in a high pressure manner in this manner. The first and second side cover parts 7, 8 are fastened to the stator 2 using coupling members 9, for example screws.

Wing grooves 10 extending in the axial direction are formed on the outer surface of the rotor 3, and wing portions 11 extending in the radial direction are disposed in each wing groove 10. Into each recess 5 a wing 11 starting from each wing groove 10 extends, which wing 11 is seated on the stator 2 in the radial direction, and in the axial direction It is seated on the side cover parts 7, 8. Each wing 11 separates the recess 5 into two interacting pressure chambers 12, 13. In order to ensure that the wing 11 is seated on the stator 2 in a high pressure sealed manner, a leaf spring member 15 is provided between the groove bottoms 14 and the wing portions 11 of the wing grooves 10. Is placed. The leaf spring member 15 applies a load to the blade portion 11 in the radial direction.

Using the first and second pressure medium lines 16, 17, the first and second pressure chambers 12, 13 may be in communication with the hydraulic pump 19 or the tank 20 by a control valve 18. Can be. By doing so, a control drive is formed, which enables the relative rotation of the stator 2 opposite the rotor 3. In this regard, all the first pressure chambers 12 are in communication with the hydraulic pump 19 and all the second pressure chambers 13 are in communication with the tank 20, or exactly the opposite configuration is formed. If the first pressure chambers 12 are in communication with the hydraulic pump 19 and the second pressure chambers 13 are in communication with the tank 20, the first pressure chambers 12 are in the second pressure chamber 13. ) In a way that collapses. From there the wing 11 is displaced in the circumferential direction, that is to say in the direction shown by the arrow 21. The rotor 3 is rotated relative to the stator 2 through the displacement of the wing 11.

The stator 2 is driven by the crankshaft through an unshown chain drive which acts on the self drive wheel 4 according to the embodiment shown. Similarly, the drive of the stator 2 using a belt drive device or a toothed gear drive device can also be considered. The rotor 3 is fastened to the camshaft, which is not shown, by a friction coupling method, a shape coupling method or a material coupling method, for example, by press-fitting or by screwing using a center fixing screw. As the rotor 3 is rotated relative to the stator 2 by the pressure medium being supplied to or discharged from the pressure chambers 12, 13, a phase shift between the camshaft and the crankshaft occurs. Therefore, by supplying or discharging the pressure medium to the pressure chambers 12, 13 as desired, the control time of the gas exchange valves of the internal combustion engine can be varied as desired.

The pressure medium lines 16, 17 are formed as channels inside the rotor 3 according to the embodiment shown, which channel the outer surface of the rotor 3 from the central bore 22 of the rotor 3. Extend toward. A central valve (not shown) may be disposed inside the central bore portion 22, through which the pressure chambers 12, 13 may communicate with the hydraulic pumps 19 to 20 as desired. Can be. In addition, a pressure medium dispensing device may be arranged in the central bore 22. The pressure medium dispensing device in this case connects the pressure medium lines 16, 17 with the pressure medium connections A, B, P, T of the externally mounted control valve 18 via the pressure medium channels and the annular grooves. Communicate.

Their lateral wall portions 6 extending essentially radially in the recesses 5 have shapes 23. These features 23 reach in the recesses 5 in the circumferential direction. The shapes 23 are used as stops for the vanes 11. And although the rotor 3 is in relation to the stator 2, the pressure chamber takes one of the two shortest positions where the wing 11 rests on the side wall on one side of the side walls 6. It is ensured by the features 23 that the fields 12, 13 can be supplied with a pressure medium.

For example, when the supply of the pressure medium to the change device 1 of the present application is insufficient during the startup phase of the internal combustion engine, the rotor 3 is uncontrolled based on the alternating torque and the drag torque that the camshaft applies to the rotor itself. In a manner relative to the stator 2. In the first step, the reaction torque of the camshaft is relative to the stator 2 in the circumferential direction opposite to the direction of rotation of the stator 2 until the rotor and stator strike the side walls 6. ) Closely. Then, the alternating torque that the camshaft applies to the rotor 3 until the pressure chamber on at least one of the pressure chambers 12, 13 is completely filled with the pressure medium is the rotor 3 and thus the recesses. (5) Causes the front and rear vibrations of the inner blades 11. This causes higher wear and noise generation in the alteration device 1 of the present application. In order to suppress this, a locking member 24 is provided in the modification apparatus 10 of the present application. To this end, a cup-shaped piston 26 is arranged in the axial bore 25 of the rotor 3. The piston 26 is loaded in the axial direction by the first spring 27. The first spring 27 is supported on one side provided to the exhaust member 28 in the axial direction, and has a cup-shaped piston 26 with its axial end facing away from the support side. It is placed inside. Within the first side cover 7, a slot link 29 is formed in such a way that the piston 26 can be fixed at that position in at least one relative position of the rotor with respect to the stator. In such a position, the piston 26 is brought into close contact with the slot link 29 by the first spring 27 when the pressure medium supply to the change device 1 of the present application is insufficient. In this state, the rotor 3 is locked in this position relative to the stator 2. In particular, the locked fixed position corresponds to a position to be taken during the start of the internal combustion engine. In addition, there is provided a means for re-adhering the piston 26 to the axial bore 26 and thus releasing the lock when the supply of the pressure medium to the alteration device 1 of the present application is insufficient. This is typically caused by using a pressure medium that is guided through the unillustrated pressure medium lines to the cavity 30 formed in the lid side tip of the piston 26. In order to guide the leaking oil from the spring chamber of the axial bore 25, the exhaust member 28 has a groove extending in the axial direction, in which the pressure medium is provided with a second side cover 8. It can be guided to the bore within.

1 further shows a hydraulic circuit 31. The pressure medium is supplied from the tank 20 to the supply connection part P of the control valve 18 using the hydraulic pump 19. At the same time the pressure medium is led from the control valve 18 to the tank 20 via the discharge connection T. The control valve 18 also has two working connections A and B, wherein the first working connection A is in communication with the first pressure chambers 12, and the second working connection B is In communication with the second pressure chambers 13. Using the electromagnetic control device 32 which reacts to the elastic force of the second spring 33, the control valve 18 can be moved to three positions. In the first position of the control valve 18 corresponding to a state in which no current flows in the control device 32, the first working connection A and thus the first pressure chambers 12 are connected to the discharge connection T. Communicating. At the same time the supply connection P is in communication with the second working connection B and hence the second pressure chambers 13. In other words, while the pressure medium is discharged from the first pressure chambers 12, the pressure medium is led to the second pressure chambers 13, whereby the wing 11 is displaced in the circumferential direction. Thereby, the phase position between the rotor 3 and the stator 2 and thereby the phase position between the camshaft and the crankshaft is changed.

In the central position, the first work connection A as well as the second work connection B are separated from the supply connection P and the discharge connection T. The pressure medium may not be supplied to or discharged from the pressure chambers 12, 13, and the phase position of the camshaft relative to the crankshaft is maintained. According to a method alternative thereto, the two working connections A, B may be in communication with the supply connection P in order to compensate for leaks occurring in the alteration device 1 herein.

In the third position of the control valve 18, the supply connection P is in communication with the first working connection A and consequently in communication with the first pressure chamber 12, on the contrary, the second pressure chamber 13. Is in communication with the discharge connection (T) through the second working connection (B). Similar to the first control position of the control valve 18, the phase position of the camshaft relative to the crankshaft is changed, but in a direction opposite to the direction at the first control position.

3 shows a control valve 101 according to the invention. The control valve 101 comprises a control device 102, a control housing 103 consisting essentially of a hollow cylinder, and a control piston 104 likewise consisting essentially of a hollow cylinder, as well as a valve housing consisting essentially of a hollow cylinder ( 105). The control housing 103 is disposed in position and fixed inside the valve housing 105. In this regard, the inner diameter of the valve housing 105 corresponds to the outer diameter of the control housing 103. In addition, the control piston 104 is disposed axially displaceable in the control housing 103, the outer diameter of the control piston 104 corresponds to the inner diameter of the control housing 103.

The valve housing 105 is disposed inside the valve receiving portion 106. The valve receiver 106 consists of two bores 107, 108, which are formed in two adjacent members 109, 110. The first adjacent member 109 is secured to the second adjacent member 110 such that the bores 107, 108 are formed and arranged in such a way that they are at least nearly coaxially positioned with one another. The inner diameter of the second bore portion 108 is configured to be smaller than the inner diameter of the first bore portion 107 according to this embodiment. As a result, a circular ring-shaped axial stop 11 is created at the interface between the first adjacent member 109 and the second adjacent member 110, and the axial stop has an insertion depth of the control valve 101. Restrict.

The valve housing 105 has a region 112 whose outer diameter decreases at the tip end side of its axial stop, and the outer diameter of the outer diameter reducing region 112 is smaller than the inner diameter of the second bore 108. In addition, according to the present embodiment, the transition portion toward the outer diameter reducing region 112 is configured in a step shape. The valve housing 105 penetrates through the first bore 107 and extends at least partially into the second bore 108 using its diameter reducing region 112. In this regard, the outer diameter of the valve housing 105 corresponds to the inner diameter of the valve receiving portion 106.

Three pressure medium channels 113 are formed at the interface between the first and second adjacent members 109, 110. The pressure medium channels 113 are configured in the form of grooves and are provided in the surface portion of the first or second adjacent member 109, 110. Each pressure medium channel 113 opens into vertical grooves 114a, 114b, 114p that are formed on the surface of the first bore 107. The vertical grooves 114a, 114b, 114p are offset from each other in the circumferential direction of the first bore 107 and extend substantially in the axial direction of the valve housing 105. Each of the vertical grooves 114a, 114b, 114p communicates with the interior of the valve housing 105 through respective radial openings 115a, 115b, 115p formed in the valve housing 105, the radial openings being the work connection. (A, B) and supply connection (P).

The outer surface of the control housing 103 has three annular grooves 116a, 116b, 116p which are arranged axially offset from each other. In this regard, the vertical grooves 114a, 114b, 114p, the radial openings 115a, 115b, 115p, and the annular grooves 116a, 116b, 116p are characterized in that the first vertical groove 114a has a first radius. Only the first annular groove 116a is communicated using the directional opening 115a, and the second vertical groove 114b is only in communication with the second annular groove 116b through the second radial opening 115b, And the third vertical groove 114p is arranged in such a manner as to communicate only with the third annular groove 116p using the third radial opening 115p. In addition, each annular groove 116a, 116b, 116p communicates with the interior of the control housing 103 using openings 117a, 117b, 117p formed in its groove bottom.

The control piston 104, which is disposed inside the control housing 103, controls the inside of the control housing 103 against the elastic force of the first spring member 120 through the push rod 119 using the control device 102. Can be displaced axially. The control piston 104 has two control sections 121, the outer edges of the control sections 121 correspond to the inner edges of the control housing 103. The control sections 121 may be manufactured as a separate structural member, assembled to the control piston 104, or may be embodied integrally with the control piston 104 as shown in FIG. 3. Outside the control sections 121, the outer diameter of the control piston 104 is configured to be smaller. The control sections 121 are configured to communicate the first or second annular grooves 116a and 116b with the third annular groove 116p according to respective positions of the control piston 104 relative to the control housing 103. Four annular grooves 122 are configured in such a way that they are arranged on the control piston 104.

In addition, the control piston 104 is configured such that its own front end side on which the first spring member 120 acts is opened. By doing so, there is communication between the interior of the control piston 104 and the second bore portion 108, whereby a discharge connection T is formed. At the push rod side end of the control piston 104, fourth openings 123 are formed, whereby the inside of the control piston 104 is in hydraulic communication with the outside of the control piston 104. The fourth openings 123 are located outside the fourth annular groove 122 provided on the outer surface of the control piston 104 in accordance with the illustrated embodiment.

Using the control device 102, the control piston 104 can be moved through the push rod 119 to each arbitrary position between the two maximums within the control housing 103. At this time, the first spring member 120 returns to the control piston 104. As the control device 102, for example, hydraulic control devices are used, or electromagnetic control devices are used as in the illustrated embodiment. The electromagnetic control device 102 consists of a coil disposed in the magnetic field of one or more permanent magnets. The coil is assigned a current supply unit through which the coil can be excited as an electrical current. In this regard, a number of possibilities for exciting the coil can be considered. For example, there may be a method of changing the coil position inside the magnetic field by varying the current intensity, in which case the high current intensity corresponds to the large deflection, and the low current strength corresponds to the small deflection. Similarly, the coil may be excited using a pulsating current. For example, a square wave voltage between a value of ₀ V and a constant voltage V ₀ may be applied to the electrode of the coil. The deflection of the coil and thus the deflection of the control piston 104 is determined by the ratio of time intervals in which no voltage V ₀ is applied to the electrode or no potential difference is applied to the electrode. The longer the interval of the no-voltage state, the smaller the deflection of the coil. The longer the time interval at which the voltage V ₀ is applied, the greater the deflection.

The embodiment according to FIGS. 3 and 4 shows a 4/3 directional control valve with four pressure medium connections A, B, P and T, with the control piston 104 being essentially in three control states. It can be located at However, the present invention is not limited to the 4/3 directional control valves, and for example, completely different embodiments in which 4/4 directional control valves or other valves are used may be considered.

In the following, the function of the 4/3 directional control valve is described according to the embodiment. Through the pressure medium channel on one side of the pressure medium channels 113, the third vertical groove 114p is supplied with the pressure medium. In each control position of the control valve 101, the pressure medium is supplied to the fourth annular groove 122 through the third radial opening 115p, the third annular groove 116p and the third opening 117p. .

In a first state of the control valve 101 corresponding to a state in which no current is supplied to the control device 102, the control piston 104 is directed toward the control device 102 by the elastic force of the first spring member 120. Displaced to the maximum deflection position. In this control position, the fourth annular groove 122 is in communication with the first vertical groove 114a through the first openings 117a, the first annular groove 116a, and the first radial opening 115a. From this vertical groove 114a the pressure medium is led to the first pressure chambers 12.

In the second control position of the control valve 101, to which the control device 102 is supplied with maximum current, the control piston 104 is maximally deflected in the direction of the first spring member 120. In this case, the fourth annular groove 122 is in communication with the third openings 117p and the second openings 117b. The pressure medium is then supplied through the second annular groove 116b, the second radial opening 115b, and the second vertical groove 114b to the corresponding pressure medium channel 113 and then to the second pressure chamber. To the field 13.

In the third state the control piston 104 is located in a central position where the fourth annular groove 122 is in communication only with the third openings 117p. In this case the pressure medium supply to both pressure chambers 12, 13 is cut off. According to an alternative method, it is also conceivable that the fourth annular groove 122 communicates with the first, second and third openings 117a, 117b, and 117p at the central position. In this case the pressure medium is led to the two pressure chambers 12, 13, whereby the leak is compensated for and the phase position between the camshaft and the crankshaft is fixed in a manner that ensures function.

In the first and second control positions, the control sections 121 completely open the respective openings 117a and 117b or close them completely. The control piston 104 can of course be positioned at each arbitrary position between the two extremes, whereby the openings 117a and 117b can only be partially opened or closed. By doing so, the perfusion resistance to the pressure chambers 12, 13 and thus the pressure medium supply can be adjusted.

To suppress the point where the pressure medium is discharged from the vertical grooves 114a, 114b, 114p directly into the second bore 108, and in particular the leakage flow between the vertical grooves 114a, 114b, 114p. A sealing member 124 is provided between the valve housing 105 and the axial stop 111 to suppress leakage flow at the interface between adjacent members 109, 110. The sealing member 124 is configured as a sealing ring capable of elastic deformation according to the illustrated embodiment, and is preferably made of fluororubber or acrylonitrile butadiene rubber. More preferably, the sealing member 124 is disposed in the outer diameter reducing area 112 of the valve housing 105. While assembling the control valve 101 to the valve housing 106, the sealing member 124 is positioned in the outer diameter reducing region 112 of the valve housing 105. Subsequently, the valve housing 105 is inserted into and fixed in the valve receiving portion 106. By placing the sealing member 124 in the outer diameter reducing area 112, the centering and guiding action is taken on the sealing member 124 during the assembly process, whereby assembly defects can be reliably avoided. By using the elastically deformable sealing member 124, the axial tolerance can be compensated for.

The sealing member 124 is pressed toward the axial stop 111 by the valve housing 105 in the assembled state. At this time, the sealing member is enclosed in a U-shape by the axial stop 111 and the stepped portion of the outer diameter reducing region 112 of the valve housing 105. The sealing member 124 is elastically deformed by the force action, and thus is pressed against the inner surface side of the valve housing 106 based on the U-shaped elongation fixation. Doing so ensures an optimum sealing action faster in the axial direction.

More preferably, the sealing member 124 is disposed in a manner adjacent to the inner surface of the valve receiving portion 106 at the interface between the two adjacent members 109, 110. By doing so, a gap, which is sometimes present in the interface, is sealed and a sealing action in the circumferential direction is also ensured.

By configuring the second bore portion 108 to have a smaller inner diameter as compared to the first bore portion 107, an axial stop 111 is formed, which axial stop into the valve receiving portion 106. It limits the insertion depth of the control valve 101 to be inserted and mounted, and acts as a sealing surface while interacting with the sealing member 124. The control valve 101 is engaged and fixed into the second bore 108 only using its outer diameter reducing area 112. Since the region 112 does not perform a sealing function through interaction with the inner surface of the second bore portion 108, the outer diameter of the region 112 is more than the inner diameter of the second bore portion 108. It can be configured small, which makes the system insensitive to tolerances.

In addition, an additional seal 125 is provided between the control housing 103 and the valve housing 105, or between the valve housing 105 and the first bore portion 107, which seal control device 102. Suppresses the flow of leakage in the direction and thus into the engine compartment.

5 and 6 show a second embodiment of the present invention. The second embodiment is the same as the first embodiment shown in Figs. 3 and 4 in a broad part. The difference to the first embodiment is that the second bore portion 108 is configured in a step shape. In this regard, the inner diameter of the first region 126 directly connected to the first bore portion 107 is configured to be larger than the inner diameter of the first bore portion 107. In addition, the inner diameter of the second region 127 connected to the first region 126 is configured to be smaller than the inner diameter of the first bore portion 107. As a result, an axial stop 111 is formed in the switching portion that is switched from the first region 126 to the second region 127. The valve housing 105 penetrates through the first bore portion 107 of the first adjacent member 109 and is engaged with and fixed in the second adjacent member 110. This is possible even if the bores 107 and 108 are only slightly offset from each other, based on the larger inner diameter of the first region 126 of the second bore 108. The diverting region 128 of the valve housing 105 which is diverted to the diameter reducing region 112 is not configured in the form of a staircase as in the first embodiment but at least partially conical in accordance with this embodiment. The sealing member 124 is configured as a sealing ring and is disposed in the switching area 128, the shape of the sealing member 124 conforming to the shape of the switching area 128, in particular to the cone 127 of the switching area. In other words, the inner surface 133 of the closure member 124 includes a first conical region 129, the inner diameter of which starts from the leading end in the axial direction until it corresponds to the outer diameter of the outer diameter reducing region 112, It continues to decrease.

A second conical region 131 is formed on the outer surface 134 of the sealing member 124, which is concave edge portion 130 offset in the axial direction toward the first conical region 129. It is configured to). The outer diameter of the sealing member 124 increases from the leading end until the maximum outer diameter of the sealing member 124 is achieved in the axial direction.

The axial length of the first region 126, the outer diameter reducing region 112, and the sealing member 124 is such that the sealing member 124 is the interface between the first adjacent member 109 and the second adjacent member 110. It is configured in such a way that it rests on the first bore 107 as well as the second bore 108.

As the conical region is provided on the outer surface of the valve housing 105, the sealing member 124 is connected to the surface of the first bore 107 and the surface of the first region 126 of the second bore 108. Seated in a sealed manner. Based on the shape of the sealing member 124, a hollow chamber 132 is formed between the second bore portion 108 and the sealing member 124. This hollow chamber allows for compensation of axial gaps that sometimes occur during assembly. The valve housing 105 can in this embodiment adhere the material of the closure member 124 into the hollow chamber 132, whereby the control valve 101 is further inserted into the valve receptacle 106 in the axial direction. It becomes possible. The hollow chamber 132 can compensate for the axial tolerance more than is possible by the sealing member 124 shown in the first embodiment.

Obviously, the sealing member 124 according to the second embodiment can be used in the valve receiving portion 106 of the first embodiment, and vice versa. In addition, the two sealing members 124 and the control valve 101 may be used in only one stepped bore portion used as the valve receiving portion 106. The sealing member 124 and the control valve 101 can likewise be inserted in the bore portion which is bounded by the radially extending wall portion in the shape of a circular ring.

7 and 8 illustrate the sealing member 124 herein in the form of a sealing ring. Each annular edge portion 130 of the inner surface 133 and the outer surface 134 of the sealing member 124 is formed conical. This conical shape is provided as the partial cross sectional shape of the closure member 124 is achieved by material polishing the two edge portions of the rectangular surface. In other words, the first conical region 129 provided on the inner surface 133 is formed in a funnel shape, and the second conical region 131 provided on the outer surface 134 is formed in a truncated cone shape.

In addition, the sealing member 124 is made of an elastomer. In this case, fluorine rubber or acrylonitrile butadiene rubber may be used as the material.

<Description of main parts of drawing>

1: (control time change) device

2: stator

3: rotor

4: driving wheel

5: recess

6: side wall

7: first side cover

8: second side cover

9: coupling member

10: wing groove

11: wing

12: first pressure chamber

13: second pressure chamber

14: groove bottom

15: leaf spring member

16: first pressure medium line

17: second pressure medium line

18: control valve

19: hydraulic pump

20: tank

21: arrow

22: center bore

23: shape

24: locking member

25: axial bore

26: piston

27: first spring

28: exhaust member

29: slotted link

30: common part

31: hydraulic circuit

32: control unit

33: second spring

A: first working connection

B: second working connection

P: supply connection

T: outlet connection

101: control valve

102: control unit

103: control housing

104: control piston

105: valve housing

106: valve compartment

107: first bore part

108: second bore fisherman

109: first adjacent member

110: second adjacent member

111: axial stop

112: area where the outer diameter decreases (outer diameter reducing area)

113: pressure medium channel

114a: first vertical groove

114b: second vertical groove

114p: third vertical groove

115a: first radial opening

115b: second radial opening

115p: third radial opening

116a: first annular groove

116b: second annular groove

116p: third annular groove

117a: first opening

117b: second opening

117p: third opening

119: push rod

120: first spring member

121: control section

122: fourth annular groove

123: fourth opening

124: sealing member

125: Shilling

126: first region

127: second area

128: transition area

129: first conical region

130: annular edge portion

131: second conical region

132: hollow chamber

133: inside

134: exterior

Claims (13)

delete delete A control valve 101 for controlling the supply and discharge of the pressure medium to the apparatus 1 for changing the control time of the internal combustion engine, A valve housing 105 which consists essentially of a cylinder and is formed with pressure medium connections A, B, P, T, A control piston 104 disposed inside the valve housing 105 and axially displaceable; Depending on the position of the control piston 104, communication between different pressure medium connections (A, B, P, T) can be realized or separated, The valve housing 105 is disposed inside the valve receiving portion 106, In the control valve 101, the insertion depth of the valve housing 105 inserted into the valve housing 106 is limited by the axial stop 111 formed in the valve housing 106, The axial stop 111 is configured as a wall in the form of a circular or circular ring, The wall extends radially inward from the inner surface of the valve receiving portion 106, A sealing member 124 is disposed between the valve housing 105 and the axial stop 111 of the valve receiving portion 106. The valve receiving portion 106 is composed of first and second bore portions 107 and 108, and the first and second bore portions 107 and 108 are formed in different adjacent members 109 and 110. , Coaxially arranged, configured in a mutually continuous manner, The axial stop 111 is formed on the interface between the different adjacent members (109, 110), The axial stop 111 is disposed and the sealing member 124 in such a manner that the sealing member 124 is seated on the boundary surface of the different adjacent members 109, 110 in the valve receiving portion 106. ) Is formed, A control valve, characterized in that a pressure medium channel (113) in communication with the interior of the valve housing is formed at the interface between the different adjacent members (109, 110). 4. The axial stop side leading end of the valve housing 105 is formed with an area 112 of which the outer diameter is reduced, and the sealing member 124 is at least partly the outer diameter reducing area 112. And a control valve disposed therein. 4. The control valve of claim 3, wherein the closure member (124) is configured as a closure ring having an outer surface (134) and an inner surface (133). 4. The control valve of claim 3, wherein the closure member (124) is made of elastomer. 7. The control valve of claim 6, wherein the elastomer is fluororubber or acrylonitrile butadiene rubber. delete delete delete delete 5. The diverting region 128 of the valve housing 105 directed to the diameter reducing region 112 is at least partially conical and the closure member 124 has its own inner surface 133. And a first conical region (129), said conical region (129) corresponding to a diverting region (128) of said valve housing (105). 13. The outer surface 134 of the closure member 124 has a second conical region 131 at the tip end thereof seated at the axial stop 111, thereby closing the closure member 124. And a ring-shaped hollow chamber (132) is formed between the axial stop (111).

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