Information
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Patent Grant
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6497215
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Patent Number
6,497,215
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Date Filed
Wednesday, October 24, 200122 years ago
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Date Issued
Tuesday, December 24, 200221 years ago
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Inventors
-
Original Assignees
-
Examiners
Agents
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CPC
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US Classifications
Field of Search
US
- 123 456
- 123 510
- 123 511
- 123 447
- 123 17916
- 123 17917
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International Classifications
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Abstract
Described is an apparatus for rapid pressure buildup in a motor vehicle reservoir-type injection system (common rail) supplied with fuel by a high-pressure pump, the apparatus including a piston, which defines a pressure chamber that can be enlarged counter to the force of a spring element prestressed counter to the piston, which pressure chamber communicates with the feed pump and with the device supplied with the pressure medium. A locking device acting on the piston is provided, by which the piston can be locked in a locking position, assumed as a result of the pressure, built up in the pressure chamber by the feed pump, counter to the prestressing of the spring element and can be untensed after unlocking into a position that reduces the size of the pressure chamber. By the relaxation of the spring, the system pressure is built up suddenly.
Description
CROSS-REFERENCE TO RELATED APPLICATIONS
This application is a 35 USC 371 application of PCT/DE 00/01726 filed on May 27, 2000.
BACKGROUND OF THE INVENTION
1. Field of the Invention
The invention is based on an apparatus for rapid pressure buildup in a motor vehicle device supplied with a pressure medium by a feed pump, in particular in a reservoir-type injection system (common rail) supplied with pressure by a high-pressure pump.
2. Description of the Prior Art
In modern internal combustion engines, high-pressure injection systems are increasingly used in which fuel is kept on hand in a storage volume at high pressure, so as to be distributed to injection valves, an example being reservoir-type injection systems (common rails) in self-igniting internal combustion engines and direction injection systems in internal combustion engines with externally supplied injection. In such high-pressure injection systems, the problem arises that even during starting of the engine, an adequately high pressure must be built up in the injection system. As a rule, the high-pressure fuel pumps used to supply the high-pressure injection systems with fuel are driven by the engine crankshaft, so that the pressure buildup at starter rpm proceeds too slowly and lengthens the starting time. Thus not only the high-pressure fuel pumps but also prefeed pumps are used, so that an adequate pressure level can be made available for starting. However, this means an increase of pollutants in the exhaust.
Furthermore, electrohydraulic valve control devices for gas exchange valves of internal combustion engines also operate at high pressure, at which hydraulic oil is brought by a hydraulic pump to a pressure level of 100 bar, for instance, for actuating gas exchange valve actuators hydraulically. Once again, the problem arises that the high pressure must already be available upon starting of the engine.
From European Patent Disclosure EP 0 455 761 B1, a hydraulic valve control device for controlling the gas exchange valves of an internal combustion engine is known, with a control pressure reservoir disposed upstream of a magnet valve and containing a piston, which defines a pressure chamber that can be increased in size counter to the force of a spring element prestressed counter to the piston. The pressure chamber of the control pressure reservoir is connected to a feed pump of the valve control device and can be made to communicate with its control lines via the magnet valve. While the magnet valve is in the closing position, the piston, because of the pressure built up in the pressure chamber by the feed pump, is forced, counter to the action of the spring element, into a position that increases the size of the pressure chamber. When the magnet valve is open, the pressure in the pressure chamber drops, because some of the hydraulic oil flows into the control lines. Because of the dropping counter pressure, the piston can decrease the size of the pressure chamber because of its spring prestressing, resulting in a pressure surge that makes it possible to make the control pressure in the control lines still more precise and to maintain that pressure.
In order beyond this originally provided purpose to make it possible also to keep high pressure available for an ensuing restart after the engine has been put out of operation, the magnet valve would have to remain closed during the entire time that the engine is off, so as to keep the pressure chamber constantly at high pressure and to keep the piston prestressed. Proceeding in this way, however, entails the problem that even the slightest leakages would mean that the high pressure in the pressure chamber would be degraded over time, and thus not enough pressure would be available for the restart of the engine. Furthermore, safety concerns advise against keeping high pressure on hand in a pressure reservoir of a motor vehicle, because if improper work is done on the pressure reservoir, accidents can happen.
SUMMARY OF THE INVENTION
The apparatus according to the invention has the advantage over the prior art that the piston used to generate a rapid pressure rise can be kept in its energy-storing position, prestressed counter to the spring element, solely by the locking device according to the invention. Thus leaks in the line system that cause a pressure loss in the pressure chamber cannot also lead to a loss of the energy stored by the piston. Since when the engine is off, because the feed pump is not in operation then, the pressure chamber is virtually without pressure anyway, if work is done on the motor vehicle there is no risk that the high pressure stored in the pressure chamber will discharge by itself.
In a preferred embodiment of the invention provides that the piston is guided longitudinally displaceably inside a closed cylinder, and the pressure chamber is formed between the piston and a bottom of the cylinder; this bottom is provided with a pressure connection, and by way of this bottom the pressure chamber is connected to a pressure line that effects communication between the feed pump and the device.
Expediently, the locking device includes two locking bolts, received in diametrically opposed receiving bores in the cylinder wall and in the outset position protruding into the cylinder in a direction transverse to the direction of motion of the piston and preferably prestressed in this direction by helical springs, which bolts can be forced back into their receiving bores by the motion of the piston in the direction of its locking position and, after the piston has moved past the bolts and reached its locking position, the bolts positively engage at least the edge of the piston, emerging from their receiving bores.
By the provisions recited, an automatic locking of the piston is attained because the pressure existing in the system assures that the piston will move past the locking bolts and push them back into their receiving bores. Once the piston has then reached its locking position, the spring-prestressed locking bolts automatically move out of the receiving bores and lock the piston.
BRIEF DESCRIPTION OF THE DRAWINGS
One exemplary embodiment of the invention is shown in the drawing and described in further detail in the ensuing description. The sole FIGURE of the drawing, in highly schematic form, shows an apparatus for rapid pressure buildup in a reservoir-type injection system (common rail) supplied with fuel by a high-pressure pump, in accordance with a preferred embodiment of the invention.
DESCRIPTION OF THE PREFERRED EMBODIMENT
In the exemplary embodiment shown in the drawing, the apparatus
1
according to the invention, serves the purpose of rapid pressure buildup in a reservoir-type injection system
4
(common rail), supplied with pressure by a high-pressure pump
2
, of a self-igniting internal combustion engine
6
of a motor vehicle.
The apparatus
1
is connected via a pressure connection
8
to a pressure line
10
, which affects communication between the high-pressure pump
2
and a distributor strip
12
, downstream of the pump, of the reservoir-type injection system
4
. The high-pressure pump
2
to this end draws fuel from a fuel tank
14
, shown highly schematically in the drawing, and supplies the distributor strip
12
with fuel at high pressure which is then distributed in a known way to individual injection valves
16
. The reservoir-type injection system
4
is disposed in the region of a cylinder head
18
of the engine
6
that is mounted on a cylinder block
20
.
In detail, the apparatus
1
has a pipe stub
26
, which is embodied in the bottom
22
of a housing
24
and is inserted into a stepped receiving bore
28
on the cylinder head
18
. A connecting conduit
30
, extending inside the pipe stub
26
and the receiving bore
28
between the apparatus
1
and the pressure line
10
, is sealed off from the atmosphere by a sealing ring
34
received in a radially outer annular conduit
32
of the pipe stub
26
. The housing is preferably embodied as an elongated cylinder
24
, in which a cup-shaped piston
40
, comprising a hollow-cylindrical piston wall
36
and a terminal piston bottom
38
, is guided longitudinally. Between the bottom
22
of the cylinder
24
and the face
42
, toward it, of the piston bottom
38
, a pressure chamber
44
is defined, which communicates constantly with the pressure line
10
via the connecting conduit
30
. The face
46
of the piston bottom
38
pointing away from the pressure chamber
44
is loaded by a helical spring
50
, which is braced on a head plate
48
of the cylinder
24
, is received partly inside the piston wall
36
, and prestresses the piston
40
into positions that decrease the size of the pressure chamber
44
.
Since the pressure chamber
44
is constantly in communication with the pressure line
10
, in which in operation of the engine
6
fuel at feed pressure is pumped to the distributor strip
12
, a correspondingly high pressure prevails in the pressure chamber
44
as well, and as a result the piston
40
is forced, counter to the action of the helical spring
50
, into positions that increase the size of the pressure chamber
44
. In order to lock the piston
40
in a locking position, represented by solid lines in the drawing, in which the pressure chamber
44
has a maximum size, defined for instance by the impact of the piston
40
on the head plate
48
of the cylinder
24
, receiving bores
54
, for instance diametrically opposite one another, are embodied in the cylinder wall
52
, and in them, locking bolts
56
are guided that are displaceable transversely to the longitudinal axis and transversely to the direction of motion of the piston
40
. Each locking bolt
56
is additionally guided in a through bore
58
, aligned with the associated receiving bore
54
of the cylinder
24
, on the bottom of a housing
60
mounted radially on the cylinder.
The locking bolts
56
are prestressed radially inward on the head end, each by a respective helical spring
64
braced on a head plate
62
of the housing
60
, and in the outset state they therefore protrude into the interior of the cylinder
24
. A shoulder
66
, whose diameter is greater than that of the receiving bore
54
, assures an impact of the locking bolts
56
on the edge of the associated receiving bore
54
. The spacing of the locking bolts
56
from the head plate
48
of the cylinder
24
is essentially equivalent to the length of the piston
40
.
As already described, starting the engine
6
drives the high-pressure pump
2
, and generates a correspondingly high fuel pressure in the pressure line
10
; this pressure is present in the pressure chamber
44
and in particular at the face
42
of the piston bottom
38
toward the pressure chamber
44
. As a result, the piston
40
moves from an outset position, represented by dot-dashed lines in the drawing, in the region of the cylinder bottom
22
in which the pressure chamber
44
is vanishingly small, the piston
40
moves counter to the prestressing action of the helical spring
50
toward the locking bolts
56
protruding into the interior of the cylinder
24
and positively displaces the locking bolts back into their receiving bores
54
until the ends
68
toward the foot of the locking bolts
56
are flush with the inside face
70
of the cylinder wall
52
. To facilitate this, the ends
68
toward the foot of the locking bolts
56
are shaped accordingly and are preferably tapered in wedgelike fashion radially inward, with the oblique wedge face
72
oriented toward the outset position of the piston
40
. The spring rate of the helical spring
50
prestressing the piston
40
is expediently selected such that the force of the spring on the piston bottom
38
is less than the oppositely oriented pressure force that results from the operating pressure of the high-pressure pump
2
. Unfortunately, it cannot be avoided that small quantities of fuel or hydraulic oil will pass between the cylinder wall
52
and the piston wall
36
. To prevent the space between the piston bottom
38
and the head plate
48
from becoming flooded with fluid, an outlet
90
with a return line
91
is provided.
Once the piston
40
has moved past the locking bolts
56
and has preferably struck the end, oriented away from the pressure chamber
44
, of the piston wall
36
at the head plate
48
of the cylinder, the locking bolts
56
are forced back out of the receiving bores
54
by the action of the helical springs
64
that prestress them, until they are seated with their shoulders
66
on the edges of the receiving bores
54
. Then preferably the outer edge of the face
42
of the piston bottom
38
oriented toward the pressure chamber
44
is positively engaged from behind by the locking bolts
56
. Since the spacing of the locking bolts
56
from the head plate
48
of the cylinder
24
is essentially equivalent to the length of the piston
40
, the piston is now fixed on both sides in its locking position.
By means of current-excitable electromagnets
74
disposed inside the housings
60
, the locking bolts
56
can be retracted, counter to the action of the helical springs
64
prestressing them radially inward, into the receiving bores
54
, at least until their ends
68
toward the foot are flush with the inside face
70
of the cylinder wall
52
. The electromagnets
74
comprise a magnet coil
76
, which radially surrounds a magnet core
78
. The locking bolts
56
then form armatures, upon which a magnetic attracting force is exerted by the delivery of current to the magnet coils
76
. A corresponding electrical signal to deliver current to the magnet coils
76
is generated, for instance by an engine control unit
80
, upon starting of the engine
6
, and as a result the piston
40
is unlocked. Since at the instant of starting no significant pressure has yet been built up by the high-pressure pump
2
, only a slight pressure still prevails in the pressure chamber
44
. For lack of a counter pressure, the unlocked piston
40
, driven by the prestressing force of the helical spring
50
, therefore presses against the fluid in the pressure chamber
44
, and as a result the pressure chamber
44
decreases in size. This creates a pressure rise in the pressure line
10
, as a result of which the fuel/oil pressure in the distributor strip
12
is rapidly brought to an adequate level.
The foregoing relates to preferred exemplary embodiments of the invention, it being understood that other variants and embodiments thereof are possible within the spirit and scope of the invention, the latter being defined by the appended claims.
Claims
- 1. An apparatus (1) for rapid pressure buildup in a motor vehicle reservoir-type injection system (common rail) (4) supplied with fuel by a high-pressure feed pump (2), the apparatus comprising a piston (40) defining a pressure chamber (44) communicating with the feed pump, said pressure chamber containing a spring element (50) prestressed counter to the piston, the piston being moveable counter to the force of the spring element (50) to enlarge the pressure chamber, a locking device (56, 64, 74) acting on and releasibly locking said piston in a locking position, assumed as a result of movement by pressure built up in said pressure chamber (44) by the feed pump (2), counter to the prestressing force of said spring element (50), means for unlocking said piston to permit movement of said piston by said spring element (50) to reduce the volume of the pressure chamber (44), said piston being guided longitudinally displaceably inside a closed cylinder (24), said pressure chamber (44) being formed between the piston (40) and a bottom wall (22) of said closed cylinder (24), said bottom wall being provided with a pressure connection connecting said pressure chamber (44) to a pressure conduit (10) affecting communication between the feed pump (2) and the common rail (4), wherein said locking device comprises two locking bolts (56), received in diametrically opposed receiving bores (56) in said closed cylinder wall (52), said locking bolts being movable between a first position protruding into the cylinder (24) in a direction transverse to the direction of motion of the piston (40) and a second position withdrawn from said cylinder, and spring means (64) biasing said locking bolts to said first position, said bolts being capable of being forced from said first to said second position by the motion of said piston (40) in a direction counter to the prestressing force of said spring element and, after said piston (40) has moved past the bolts and reached said first position, wherein the bolts positively engage and releasibly retain said piston (40) to retain said piston.
- 2. The apparatus of claim 1, wherein said closed cylinder comprises a closed head plate (48), and wherein the spacing of the locking bolts (56) from said head plate (48) is essentially equivalent to the length of the piston (40).
- 3. The apparatus of claim 2, wherein said piston (40) is cup-shaped, with a hollow- cylindrical piston wall (36) and a terminal piston bottom (38), and wherein said spring element, is a helical spring (50), received inside the piston wall (36) and is fastened between the piston bottom (38) and said head plate (48) of the cylinder (24).
- 4. The apparatus of claim 1, wherein said closed cylinder comprises a closed head plate (48), and further comprising a pressure relief bore (90) in said head plate (48) to permit leakage fluid to flow out of said closed cylinder (24).
- 5. The apparatus of claim 4, wherein said locking device further comprises current-excitable electromagnets (74) operable to more said locking bolts (56), from the first position to the second position against the face of said spring means for unlocking said piston (40).
- 6. The apparatus of claim 5, wherein said electromagnets (74) each include one magnet coil (76) radially surrounding a magnet core, and wherein said locking bolts (56) form armatures, upon which, by the delivery of electric current to the magnet coils (76), a magnetic attraction force can be exerted.
- 7. The apparatus of claim 6, wherein said electromagnets (74) are excited by current upon starting of the motor vehicle.
Priority Claims (1)
Number |
Date |
Country |
Kind |
199 49 514 |
Oct 1999 |
DE |
|
PCT Information
Filing Document |
Filing Date |
Country |
Kind |
PCT/DE00/01726 |
|
WO |
00 |
Publishing Document |
Publishing Date |
Country |
Kind |
WO01/27467 |
4/19/2001 |
WO |
A |
US Referenced Citations (10)
Foreign Referenced Citations (1)
Number |
Date |
Country |
42 15 721 |
Nov 1993 |
DE |