Technical Field
[0001] The present invention relates to a valve timing control apparatus used for controlling
opening/closing timing of an exhaust valve or an intake value in a valve operated
device of an internal combustion engine and especially a valve timing control apparatus
according to the preamble of the patent claim 1.
Background Art
[0002] Conventionally, as an example of a valve timing control apparatus, there is disclosed
an apparatus including a rotation transmitting member rotatably mounted on a valve
opening/closing rotational shaft to be rotatable relative thereto over a predetermined
range and receiving a rotational drive force from a crank pulley, a vane mounted on
a rotational shaft comprised of a cam shaft and an inner rotor provided integrally
therewith, a fluid pressure chamber formed between the rotational shaft and the rotation
transmitting member and divided into an advanced angle chamber and a retarded angle
chamber, a first fluid passageway for feeding/discharging fluid to/from the advanced
angle chamber, a second fluid passageway for feeding/discharging fluid to/from the
retarded angle chamber, a retracting hole formed in the rotation transmitting member
for receiving therein a lock pin urged toward the rotational shaft, a receiving hole
formed in the rotational shaft for receiving the head of the lock pin when the rotational
shaft and the rotation transmitting member come into a predetermined phase synchronization
or registry with each other, and a third fluid passageway for feeding/discharging
fluid to/from this receiving hole (see e.g. Patent Document 1).
[0003] The invention described in Patent Document 1 provides a first switching valve for
controlling feeding/discharging of the fluid to/from the first fluid passageway and
the second fluid passageway and a second switching valve for controlling feeding/discharging
of the fluid to/from the third fluid passageway, so that the feeding/discharging of
the fluid to/from the third fluid passageway may take place independently of the feeding/discharging
of the fluid to/from the first and second fluid
According to document D2 a valve timing control apparatus is known comprising:
an inner rotor rotatable in unison with a valve opening/closing rotational shaft of
an internal combustion engine;
an outer rotor mounted to be rotatable relative to said inner rotor over a predetermined
range and rotatable by a force transmitted thereto from a crank shaft of the internal
combustion engine;
a fluid pressure chamber formed between said inner rotor and said outer rotor and
divided by a partitioning portion into an advanced angle chamber and a retarded angle
chamber;
a first fluid passageway for feeding/discharging fluid to/from said advanced angle
chamber;
a second fluid passageway for feeding/discharging fluid to/from said retarded angle
chamber;
a locking mechanism capable of locking relative rotation between said inner rotor
and said outer rotor;
a third fluid passageway for feeding fluid to said locking mechanism to cause this
locking mechanism to release its locking state and discharging fluid from said locking
mechanism to cause this locking mechanism to provide the locking state;
a first switching valve for controlling the feeding/discharging of the fluid to/from
said first fluid passageway and said second fluid passageway;
a second switching valve for controlling the feeding/discharging of the fluid to/from
said third fluid passageway;
a pump for feeding fluid to said first switching valve and said second switching valve;
and
a check valve for inhibiting communication of the fluid from said first switching
valve to said second switching valve and allowing communication of the fluid from
said second switching valve to said first switching valve.
Prior Art Document
Patent Document
Summary of the Invention
Object to be Achieved by Invention
[0005] However, with such valve timing control apparatus as disclosed in D1, torque variation
which the cam shaft receives from the intake valve or the exhaust valve when this
intake or exhaust valve is driven to be opened or closed is transmitted to the vane,
which results in application of torque variation alternately to the inner rotor to
the retarded angle side and to the advanced angle side, relative to the outer rotor.
[0006] For instance, let us suppose a case when fluid is fed to the advanced angle chamber
to vary the phase of the cam shaft relative to the crank shaft from the retarded angle
side to a target phase on the advanced angle side. In this case, if the inner rotor
is exposed to torque variation to the retarded angle side, this torque variation results
in displacement of the inner rotor to the direction for decreasing the volume of the
advanced angle chamber. As a result, the fluid inside the advanced angle chamber is
subject to an outflowing force from this advanced angle chamber. Conversely, if the
inner rotor is exposed to torque variation to the advanced angle side, this torque
variation results in displacement of the inner rotor to the direction for increasing
the volume of the advanced angle chamber. As a result, the advanced angle chamber
generates a force to draw in the fluid. Pulsating displacements due to such torque
variations described above will occur conspicuously in particular when the pressure
of the fluid fed from the pump is low. And, this phenomenon occurs also in the course
of switchover of the phase of the cam shaft relative to the crank shaft to a target
phase on the retarded angle side from the advanced angle side.
[0007] If the pulsating pressure of fluid due to torque variation of the cam is applied
to the locking mechanism from the advanced angle chamber and/or the retarded angle
chamber through the first fluid passageway and/or the second fluid passageway, the
first switching valve, the second switching valve and the third fluid passageway,
a pressure drop due to the pulsating pressure may lower a lock released state maintaining
pressure of the lock mechanism, as a result of which the locking mechanism may be
brought into its locking state inadvertently.
[0008] In the case of a valve timing control apparatus of the so-called "intermediate locking
type" configured such that the relative phase between the rotational shaft and the
rotation transmitting member is locked at an intermediate phase between the most advanced
angle phase and the most retarded angle phase, a lock pin provided as a restricting
member for the locking mechanism pivots about the outer periphery of a receiving hole
while this lock pin is being accommodated within a retracting hole. Under this condition,
if there occurs pulsation in the fluid pressure used for holding the lock pin in the
receiving hole, the pressure pulsation will cause repeated exit and entry (retraction)
of the pin from/into the retracting hole. As a result, the lock pin may accidentally
enter the receiving hole, thus providing a locked state.
[0009] The object of the present invention is to provide a valve timing control apparatus
capable of avoiding inadvertent realization of a locked state by effectively preventing
pulsating pressure of fluid generated in association with torque variation of a cam
shaft from having any effect on a fluid passageway for lock releasing, thereby to
restrict occurrence of inadvertent realization of the locked state during driving
of the internal combustion engine.
Solution for Accomplishing the Object
[0010] According to the first characterizing feature of a valve timing control apparatus,
the apparatus comprises:
an inner rotor rotatable in unison with a valve opening/closing rotational shaft of
an internal combustion engine;
an outer rotor mounted to be rotatable relative to said inner rotor over a predetermined
range and rotatable by a force transmitted thereto from a crank shaft of the internal
combustion engine;
a fluid pressure chamber formed between said inner rotor and said outer rotor and
divided by a partitioning portion into an advanced angle chamber and a retarded angle
chamber;
a first fluid passageway for feeding/discharging fluid to/from said advanced angle
chamber;
a second fluid passageway for feeding/discharging fluid to/from said retarded angle
chamber;
a locking mechanism capable of locking relative rotation between said inner rotor
and said outer rotor;
a third fluid passageway for feeding fluid to said locking mechanism to cause this
locking mechanism to release its locking state and discharging fluid from said locking
mechanism to cause this locking mechanism to provide the locking state;
a first switching valve for controlling the feeding/discharging of the fluid to/from
said first fluid passageway and said second fluid passageway;
a second switching valve for controlling the feeding/discharging of the fluid to/from
said third fluid passageway;
a pump for feeding fluid to said first switching valve and said second switching valve;
and
a check valve for inhibiting communication of the fluid from said first switching
valve to said second switching valve and allowing communication of the fluid from
said second switching valve to said first switching valve.
[0011] With the characterizing feature described above, there is provided a check valve
that inhibits communication of the fluid from the first switching valve to the second
switching valve and allows communication of the fluid from the second switching valve
to the first switching valve. Therefore, it is possible to prevent pulsating pressure
that occurs in association with torque variation in the rotational shaft from being
transmitted from the first switching valve to the second switching valve. Hence, stable
fluid free from the influence of the pulsating pressure can be fed from the second
switching valve to the third fluid passageway. As a result, the locking mechanism
can effectively maintain its lock-released state by this stable fluid pressure and
the inadvertent locking of the mechanism can be avoided.
[0012] According to the second characterizing feature, the fluid fed from said pump can
be fed to said first switching valve with bypassing said second switching valve and
can be fed to said second switching valve with bypassing said first switching valve.
[0013] With the characterizing feature described above, passage resistance of the first
switching valve and the passage resistance of the second switching valve do not affect
each other. Hence, controlling operation of rotational phase and controlling operations
of the locking mechanism can be effected more speedily.
[0014] According to the third characterizing feature, the fluid fed from said pump can be
fed to said first switching valve through said check valve and can be fed to said
second switching valve with bypassing said check valve.
[0015] With the characterizing feature described above, since the check valve is interposed
between the pump and the first switching valve, it is possible to prevent pulsating
pressure of the fluid occurring due to torque variation in the rotational shaft from
being transmitted to the pump. Therefore, the pulsating pressure will not affect the
second switching valve via the pump. As a result, the locking mechanism can effectively
maintain its lock-released state by this even more stable fluid pressure.
[0016] According to the additional first characterizing feature of the invention, the apparatus
further comprises:
a first connecting passageway for connecting said pump to said first switching valve;
and
a second connecting passageway for connecting a branching point of said first connecting
passageway to said second switching valve;
wherein said check valve is disposed between said branching point and said first switching
valve.
[0017] With the characterizing feature described above, passage resistance of the first
switching valve and the passage resistance of the second switching valve do not affect
each other. Hence, controlling operation of rotational phase and controlling operations
of the locking mechanism can be effected more speedily. At the same time, the pulsating
pressure does not affect the second switching valve via the pump. As a result, the
locking mechanism can effectively maintain its lock-released state by this even more
stable fluid pressure.
[0018] According to the fifth characterizing feature of the present invention, an aperture
area of said check valve when the fluid is being fed from said pump to said first
switching valve is greater than a passageway aperture area of said first connecting
passageway.
[0019] Normally, presence of a check valve within a passageway in which fluid flows provides
a passageway resistance, so that an amount of fluid needed for relative rotational
movement between the inner rotor and the outer rotor may not be fed speedily to the
fluid pressure chamber. With the inventive feature described above, since the aperture
area of the check valve when the fluid is being fed from the pump to the first switching
valve is greater than a passageway aperture area of the first connecting passageway,
the presence of the check valve does not hinder speedy supply of the fluid to the
fluid pressure chamber.
[0020] According to the additional first characterizing feature of the present invention,
the passageway aperture area of said first connecting passageway is greater than the
passageway aperture area of said second connecting passageway.
[0021] At the time of a normal advanced/retarded angle control operation, the locking mechanism
is maintained under its lock-released state, so the second connecting passageway is
maintained under its fluid flowing state. On the other hand, there occurs constant
and frequent change in the fluid flowing condition in the first connecting passageway
since this first connecting passageway is used for switching over between the advanced
angle control and the retarded angle control. Therefore, there exists higher need
to supply fluid to the first connecting passageway more readily than to the second
connecting passageway. With the characterizing feature described above, since the
passageway aperture area of the first connecting passageway is made greater than the
passageway aperture area of the second connecting passageway, fluid can be fed more
readily to the first connecting passageway, so that the advanced angle control and
the retarded angle control can be effected speedily.
Brief Description of the Drawings
[0022]
[Fig. 1] is a general construction diagram showing an embodiment of a valve timing
control apparatus relating to the present invention,
[Fig. 2] is a general construction diagram showing the valve timing invention,
[Fig. 2] is a general construction diagram showing the valve timing control apparatus
under its locking state,
[Fig. 3] is a general construction diagram showing the valve timing control apparatus
under its lock-releasing state,
[Fig.4] is a general construction diagram showing the valve timing control apparatus
under its most advanced angle state, and
[Fig.5] is a general construction diagram showing the valve timing control apparatus
under its most retarded angle state.
Modes of Embodying the Invention
[0023] Next, embodiments of the present invention will be described with reference to the
accompanying drawings. A valve timing control apparatus of the invention shown in
Fig. 1 and Fig. 2 includes a driven rotational body consisting essentially of a cam
shaft ("rotational shaft") 10, an inner rotor 30 and vanes (partitioning portions)
50 attached to the inner rotor 30, and a driving rotational body consisting essentially
of an outer rotor 40 rotatably mounted on the driven rotational body to be rotatable
relative thereto over a predetermined range, lock plates 60a, 60b, a timing sprocket
70, etc. The outer periphery of the cam shaft 10 is rotatably supported by a cylinder
head 81. Further, as well-known, the timing sprocket 70 is configured to receive a
rotational force in the clockwise direction in Fig. 2 from a crank shaft (not shown)
via a timing chain (not shown).
[0024] The cam shaft 10 includes a cam (not shown) which per se is well known, for opening/closing
an intake valve (not shown) or an exhaust valve (not shown). As shown in Fig. 1 and
Fig. 2, inside the cam shaft 10, there are formed an advanced angle passageway 11,
a retarded angle passageway 12 and a pilot passageway 13 extending along the axial
direction. The advanced angle passageway 11 is formed within an attaching hole for
an attaching bolt 16 provided in the cam shaft 10, and this passageway 11 is connected
to a connection port 101 of a first switching valve 100 via an annular passageway
91 and a connecting passageway 92 provided on the outer peripheral side of the supported
portion of the cam shaft 10. The retarded angle passageway 12 is connected to a connection
port 102 of the first switching valve 100 via an annular passageway 93 and a connecting
passageway 94 also provided on the outer peripheral side of the supported portion
of the cam shaft 10. The pilot passageway 13 is connected to a connection port 111
of a second switching valve 110 via an annular passageway 95 and a connecting passageway
96 also provided on the outer peripheral side of the supported portion of the cam
shaft 10.
[0025] The first switching valve 100 is controlled for its switching operations by a controller
(not shown). Under the condition shown in Fig. 1 and Fig. 2 wherein the valve 100
is switched to an angle advanced position (energized state), a supply port 103 connected
to an oil pump 120 via a check valve 140 is connected and communicated to the connection
port 101 and also the connection port 102 is connected and communicated to an exhaust
port 104 connected to an oil pan 130. Further, under the condition (non-energization)
wherein the valve 100 is switched to the most retarded angle position shown on the
right hand in the figure, the supply port 103 is connected and communicated to the
connection portion 102 and also the connection port 101 is connected and communicated
to the exhaust port 104.
[0026] Therefore, under the advanced angle position state described above, an amount of
oil is fed from the oil pump 120 via the check valve 140 to the advanced angle passageway
11 and also an amount of oil is discharged from the retarded angle passageway 12 to
the oil pan 130. On the other hand, under a state of retarded angle position, an amount
of oil is fed from the oil pump 120 via the check valve 140 to the retarded angle
passageway 12 and also an amount of oil is discharged from the advanced angle passageway
11 to the oil pan 130.
[0027] The second switching valve 110 is controlled for its switching operations by the
controller (not shown). Under the condition shown in Fig. 1 wherein the valve 110
is switched to the feeding position (energized state), the connection port 111 is
connected and communicated to the supply port 114 connected to the oil pump 120 and
at the same time, its communication to an exhaust port 113 connected to the oil pan
130 is blocked. Further, under the condition shown in Fig. 2 wherein the valve 110
is switched to the exhausting position (non-energized state), the connection port
111 is connected and communicated to the exhaust port 113 whereas the supply port
114 is blocked. Therefore, under this supplying position condition, oil is supplied
to the pilot passageway 13 and under the exhausting position condition, oil is discharged
through the pilot passageway 13 to the oil pan 130.
[0028] The inner rotor 30 is fixedly and integrally attached to the cam shaft 10 by the
bolt 16 and includes vane grooves 31 for allowing attachment of the four respective
vanes 50 along the radial direction. Further, the inner rotor 30 includes also a receiving
groove 32, a connecting passageway 33 connecting the bottom of the receiving groove
32 to the pilot passageway 13, a connecting passageway 34 connecting an advanced angle
chamber R1 sectioned by each vane 50 and the advanced angle passageway 11 and a connecting
passageway 37 connecting a retarded angle chamber R2 sectioned by each vane 50 and
the retarded angle passageway 12. Incidentally, each vane 50 is urged in the radially
outward direction by means of a spring 51 mounted on the bottom of the vane groove
31. The receiving groove 32 is a groove for receiving a head of the lock plate 60a,
60b by a predetermined engagement amount under the condition shown in Fig. 2, i.e.
the condition wherein the relative phases of the driven rotational body such as the
cam shaft 10, the inner rotor 30, etc. and the driving rotational body such as the
outer rotor 40, the timing sprocket 70, etc. come into synchronization or registry
with each other at a predetermined phase (an intermediate phase between the most advanced
angle phase and the most retarded angle phase suitable for startup of the internal
combustion engine).
[0029] The outer rotor 40 is assembled to the outer periphery of the inner rotor 30 to be
rotatable relative thereto over a predetermined range. And, on opposed sides of the
outer rotor 40, a front plate 41 and a rear plate 42 are integrally fastened by means
of a bolt 43. Further, in the outer rotor 40, there are formed, by the inner rotor
30, a plurality of operational chambers R0 each of which accommodates the vane 50
corresponding thereto and which is divided into an advanced angle chamber R1 and a
retarded angle chamber R2. Still further, in the outer rotor 40 along its radial direction,
there are formed retracting grooves 46a, 46b for accommodating the lock plates 60a,
60b and springs 61a, 61b for urging these plates 60a, 60b toward the inner rotor 30.
[0030] The lock plates 60a, 60b are engaged in the retracting grooves 46a, 46b to be movable
along the radial direction of the outer rotor 40 and are urged by the springs 61a,
61b toward the inner rotor 30. The springs 61a, 61b are compression springs interposed
between the lock plates 60a, 60b and retainers 62a, 62b and these retainers 62a, 62b
are fixedly assembled to the outer rotor 40.
[0031] Next, operations of the valve timing control apparatus having the above-described
construction of the instant embodiment will be described. At the time of startup of
the internal combustion engine, the engine is started up under the condition shown
in Fig. 2, that is, the condition wherein the heads of the lock plates 60a, 60b are
engaged and locked within the receiving grooves 32 at a predetermined phase suitable
for startup of the internal combustion engine. Upon startup of the internal combustion
engine, the oil pump 120 is driven to start feeding of an amount of oil. The oil discharged
from the oil pump 120 is supplied via the check valve 140 from the supply port 103
of the first switching valve 100 through the connection port 101, the connecting passageway
92, the annular passageway 91, the advanced angle passageway 11, the connecting passageway
34 to the advanced angle chamber R1. On the other hand, an amount of oil fed from
the oil pump 120 to the second switching valve 110 is not supplied to the pilot passageway
13 because the supply port 114 of the second switching valve 110 is currently blocked,
so a locking state is maintained.
[0032] After the startup of the internal combustion engine, once the second switching valve
110 is energized by a signal from a controller (not shown), as shown in Fig. 3, oil
discharged from the oil pump 120 is supplied from the supply port 114 of the second
switching valve 110 through the connection port 111, the connecting passageway 96,
the annular passageway 95, the pilot passageway 13 and the connecting passageway 33
to the receiving groove 32. Upon this supply of oil to the receiving groove 32, the
lock plates 60a, 60b are pushed radially outward against the springs 61a, 61b to move
out of the receiving grooves 32 and then are retracted into the retracting grooves
46a, 46b respectively. In this way, the locking state by the lock plates 60a, 60b
is released, whereby the driven rotational body or components such as the cam shaft
10, the inner rotor 30, the vanes 50, etc. become rotatable relative to the driving
rotational body such as the outer rotor 40, etc.
[0033] Further, under the condition shown in Fig. 3 wherein the locking by the lock plates
60a, 60b is released, if an amount of oil is supplied from the oil pump 120 through
the first switching valve 100, the advanced angle passageway 11, etc. into the advanced
angle chamber R1, an amount of oil is discharged from the retarded angle chamber R2
through the retarded angle passageway 12 and the switching valve 100, etc. to the
oil pan 130. In response to this, the driven rotational body including the cam shaft
10, the inner rotor 30 and the vanes 50, etc. is rotated clockwise in Fig. 3 relative
to the driving rotational body including the outer rotor 40, etc., thus providing
a condition shown in Fig. 4, i.e. the condition of the most advanced angle wherein
the volume of the retarded angle chamber R2 is rendered minimum.
[0034] Further, under the most advanced angle condition shown in Fig. 4, if the first switching
valve 100 is energized by a signal from the controller (not shown), as shown in Fig.
5, the amount of oil discharged from the oil pump 120 is supplied via the check valve
140 from the supply port 103 of the first switching valve 100 through the connection
port 102, the connecting passageway 94, the annular passageway 93, the retarded angle
passageway 12 and the connecting passageway 37 to the retarded angle chamber R2. On
the other hand, an amount of oil is discharged from the advanced angle chamber R1
through the advanced angle passageway 11, the switching valve 100, etc. into the oil
pan 130. In response to this, the driven rotational body including the cam shaft 10,
the inner rotor 30 and the vanes 50, etc. is rotated counterclockwise in Fig. 4 relative
to the driving rotational body including the outer rotor 40, etc., thus providing
a condition shown in Fig. 5, i.e. the condition of the most retarded angle wherein
the volume of the advanced angle chamber R1 is rendered minimum.
[0035] During driving of the internal combustion engine, in accordance with the operational
conditions of the internal combustion engine, the valve opening/closing timing is
controlled to an optimal phase as shuttling between the most advanced angle state
and the most retarded angle state. In this, in the case of transition from the most
advanced angle state shown in Fig. 4 to the most retarded angle state shown in Fig.
5, the condition of the lock plate 60a accommodated in the retracting groove 46a is
maintained. Conversely, in the case of transition from the most retarded angle state
shown in Fig. 5 to the most advanced angle state shown in Fig. 4, the condition of
the lock plate 60b accommodated in the retracting groove 46b needs to be maintained.
[0036] In the instant embodiment, in the connecting passageway between the first switching
valve 100 for controlling feeding/discharging of oil to/from the advanced angle passageway
11 and the retarded angle passageway 13 and the oil pump 120 for discharging oil,
there is incorporated the check valve 140 which allows communication of oil to the
first switching valve 100 and inhibits (checks) communication of oil to the oil pump
120. And, the second switching valve 110 for controlling feeding/discharging of oil
to/from the pilot passageway 13 is connected to the oil pump 120 via the second connecting
passageway 84 branched from a branching point 83 of the first connecting passageway
82 connecting between the oil pump 120 and the check valve 140. Therefore, by the
check valve 140, pulsating pressure of oil that occurs due to torque variation in
the cam shaft 10 can be prevented from being transmitted from the first switching
valve 100 to the oil pump 120. Further, since the second switching valve 110 is supplied
with oil through the second connecting passageway 84 branched from the first connecting
passageway 82 connecting between the oil pump 120 and the check valve 140, the second
switching valve 110 is free from any effect of the pulsating pressure of oil that
occurs due to torque variation in the cam shaft 10. So that, the oil can be supplied
in a stable manner from this second switching valve 110 to the pilot passageway 13.
As a result, the stable oil can be supplied to the receiving groove 32, so that the
condition of the lock plates 60a, 60b being accommodated within the retracting grooves
46a, 46b can be maintained, thereby to prevent occurrence of inadvertent locking.
[0037] In order to reduce the effect of passageway resistance due to the presence of the
check valve 140 so as to allow speedy supply of oil to the operational chamber R0
for achieving smooth advanced/retarded angle control operations, it is preferred that
the aperture area of the check valve 140 be greater than the passageway aperture area
of the first connecting passageway 82. Further, for preferential supply of oil to
the operational chamber R0 during the advanced/retarded angle control operations,
it is preferred that the passageway aperture area of the first connecting passageway
82 be greater than the passageway aperture area of the second connecting passageway
84.
[0038] Incidentally, in the foregoing description of the embodiment, there has been described
the case of the predetermined phase being an intermediate phase between the most advanced
angle phase and the most retarded angle phase suitable for startup of the internal
combustion engine. However, the invention is not limited thereto. Instead, the "predetermined
phase" can be the most retarded angle phase or the most advanced angle phase, as a
matter of course.
Industrial Applicability
[0039] The present invention is applicable to a valve timing control apparatus used for
controlling opening/closing timing of an exhaust valve or an intake value in a valving
device of an internal combustion engine.
Description of Reference Marks/Numerals
[0040]
10....... |
cam shaft (rotational shaft) |
11....... |
advanced angle passageway (first fluid passageway) |
12....... |
retarded angle passageway (second fluid passageway) |
13....... |
pilot passageway (third fluid passageway) |
30....... |
inner rotor |
32....... |
receiving groove (lock mechanism) |
40....... |
outer rotor |
41....... |
front plate |
42....... |
rear plate |
46a, 46b..... |
retracting grooves |
50....... |
vanes (partitioning portions) |
60a, 60b..... |
lock plates (lock mechanism) |
81....... |
cylinder head |
82....... |
first connecting passageway |
83....... |
branching point |
84....... |
second connecting passageway |
100..... |
first switching valve |
110..... |
second switching valve |
120...... |
oil pump (pump) |
130...... |
oil pan |
140..... |
check valve |
R0...... |
operational chamber (fluid pressure chamber) |
R1...... |
advanced angle chamber |
R2...... |
retarded angle chamber |
1. Ventilzeitsteuervorrichtung, mit:
einem inneren Rotor (30), der unisono mit einer drehenden Ventilöffnungs-/schließwelle
(10) einer Brennkraftmaschine drehbar ist;
einem äußeren Rotor (40), der montiert ist, um über einen vorbestimmten Bereich zu
dem inneren Rotor (30) relativ drehbar zu sein und durch eine Kraft drehbar zu sein,
die von einer Kurbelwelle der Brennkraftmaschine dazu übertragen wird;
einer Fluiddruckkammer (20), die zwischen dem inneren Rotor (30) und dem äußeren Rotor
(40) ausgebildet ist, und durch einen Teilungsabschnitt (50) in eine Vorlaufwinkelkammer
(21) und eine Verzögerungswinkelkammer (22) geteilt ist;
einem ersten Fluiddurchtrittsweg (11), um ein Fluid zu/von der Vorlaufwinkelkammer
(21) zuzuführen/abzugeben,
einem zweiten Fluiddurchtrittsweg (12), um ein Fluid zu/von der Verzögerungswinkelkammer
(22) zuzuführen/abzugeben,
einem Sperrmechanismus (60a, 60b), der in der Lage ist, eine relative Drehung zwischen
dem inneren Rotor (30) und dem äußeren Rotor (40) zu sperren;
einem dritten Fluiddurchtrittsweg (13), um ein Fluid zu dem Sperrmechanismus (60a,
60b) zuzuführen, um zu verursachen, dass dieser Sperrmechanismus (60a, 60b) seinen
Sperrzustand freigibt, und das Fluid von dem Sperrmechanismus (60a, 60b) abzugeben,
um zu verursachen, dass dieser Sperrmechanismus (60a, 60b) den Sperrzustand bereitstellt;
einem ersten Schaltventil (100), um die Zufuhr/Abgabe des Fluids zu/von dem ersten
Fluiddurchtrittsweg (11) und dem zweiten Fluiddurchtrittsweg (12) zu steuern;
einem zweiten Schaltventil (110), um die Zufuhr/Abgabe des Fluids zu/von dem dritten
Fluiddurchtrittsweg (13) zu steuern;
einer Pumpe (120), um ein Fluid zu dem ersten Schaltventil (100) und dem zweiten Schaltventil
(110) zuzuführen;
einem Sperrventil (140), um eine Kommunikation des Fluids von dem ersten Schaltventil
(100) zu dem zweiten Schaltventil (110) zu unterbinden und eine Kommunikation des
Fluids von dem zweiten Schaltventil (110) zu dem ersten Schaltventil (100) zu gestatten,
und
einem ersten Verbindungsdurchtrittsweg, um die Pumpe mit dem ersten Schaltventil zu
verbinden; und
einem zweiten Verbindungsdurchtrittsweg, um einen Abzweigungspunkt des ersten Verbindungsdurchtrittswegs
mit dem zweiten Schaltventil zu verbinden;
wobei das Sperrventil zwischen dem Abzweigungspunkt und dem ersten Schaltventil bereitgestellt
ist, dadurch gekennzeichnet, dass die Durchtrittswegsöffungsfläche des ersten Verbindungsdurchtrittswegs (82) größer
als die Durchtrittswegsöffungsfläche des zweiten Verbindungsdurchtrittswegs (84) ist.
2. Ventilzeitsteuervorrichtung nach Anspruch 1, wobei das von der Pumpe (120) zugeführte
Fluid mit einem Umgehen des zweiten Schaltventils (110) zu dem ersten Schaltventil
(100) zugeführt werden kann und mit einem Umgehen des ersten Schaltventils (100) zu
dem zweiten Schaltventil (110) zugeführt werden kann.
3. Ventilzeitsteuervorrichtung nach Anspruch 1, wobei das von der Pumpe (120) zugeführte
Fluid durch das Sperrventil (140) zu dem ersten Schaltventil (100) zugeführt werden
kann und mit Umgehen des Sperrventils (140) zu dem zweiten Schaltventil (110) zugeführt
werden kann.
4. Ventilzeitsteuervorrichtung nach Anspruch 1, wobei eine Öffnungsfläche des Sperrventils,
wenn das Fluid von der Pumpe zu dem ersten Schaltventil zugeführt wird, größer als
eine Durchtrittswegsöffungsfläche des ersten Verbindungsdurchtrittswegs ist.
1. Contrôleur de temporisation de soupape comprenant :
un rotor interne (30) pouvant tourner à l'unisson avec un arbre de rotation d'ouverture/fermeture
de soupape (10) d'un moteur à combustion interne ;
un rotor externe (40) monté pour pouvoir tourner par rapport audit rotor interne (30)
sur une plage prédéterminée et pouvoir tourner grâce à une force transmise à ce dernier
par un vilebrequin du moteur à combustion interne ;
une chambre de pression de fluide (20) formée entre ledit rotor interne (30) et ledit
rotor externe (40) et divisée par une partie de séparation (50) en une chambre angulaire
avancée (21) et une chambre angulaire retardée (22) ;
une première voie de passage de fluide (11) pour amener/décharger le fluide à/de ladite
chambre angulaire avancée (21) ;
une deuxième voie de passage de fluide (12) pour amener/décharger le fluide à/de ladite
chambre angulaire retardée (22) ;
un mécanisme de verrouillage (60a, 60b) capable de verrouiller la rotation relative
entre ledit rotor interne (30) et ledit rotor externe (40) ;
une troisième voie de passage de fluide (13) pour amener le fluide audit mécanisme
de verrouillage (60a, 60b) afin d'amener ce mécanisme de verrouillage (60a, 60b) à
débloquer son état de verrouillage et à décharger le fluide dudit mécanisme de verrouillage
(60a, 60b) pour amener ce mécanisme de verrouillage (60a, 60b) à fournir l'état de
verrouillage ;
une première soupape de commutation (100) pour commander l'amenée/décharge du fluide
à/de ladite première voie de passage de fluide (11) et de ladite seconde voie de passage
de fluide (12) ;
une seconde soupape de commutation (110) pour commander l'amenée/décharge du fluide
à/de ladite troisième voie de passage de fluide (13) ;
une pompe (120) pour amener le fluide à ladite première soupape de commutation (100)
et ladite seconde soupape de commutation (110) ;
une soupape de non-retour (140) pour empêcher la communication du fluide de ladite
première soupape de commutation (100) à ladite seconde soupape de commutation (110)
et permettre la communication du fluide de ladite seconde soupape de commutation (110)
à ladite première soupape de commutation (100), et
une première voie de passage de raccordement pour raccorder ladite pompe à ladite
première soupape de commutation ; et
une seconde voie de passage de raccordement pour raccorder un point de bifurcation
de ladite première voie de passage de raccordement à ladite seconde soupape de commutation
;
dans lequel ladite soupape de non-retour est disposée entre ledit point de bifurcation
et ladite première soupape de commutation, caractérisé en ce que la surface d'ouverture de la voie de passage de ladite première voie de passage de
raccordement (82) est supérieure à la surface d'ouverture de voie de passage de ladite
seconde voie de passage de raccordement (84).
2. Contrôleur de temporisation de soupape selon la revendication 1, dans lequel le fluide
alimenté à partir de ladite pompe (120) peut être amené à ladite première soupape
de commutation (100) en contournant ladite seconde soupape de commutation (110) et
peut être amené à ladite seconde soupape de commutation (110) en contournant ladite
première soupape de commutation (100).
3. Contrôleur de temporisation de soupape selon la revendication 1, dans lequel le fluide
alimenté à partir de ladite pompe (120) peut être amené à ladite première soupape
de commutation (100) par le biais de ladite soupape de non-retour (140) et peut être
amené à ladite seconde soupape de commutation (110) en contournant ladite soupape
de non-retour (140).
4. Contrôleur de temporisation de soupape selon la revendication 1, dans lequel une surface
d'ouverture de ladite soupape de non-retour lorsque le fluide est amené de ladite
pompe à ladite première soupape de commutation est supérieure à une surface d'ouverture
de voie de passage de ladite première voie de passage de raccordement.