DE102015203515A1 - Partial pressure compensated pressure control valve for a high-pressure accumulator - Google Patents

Abstract

The invention relates to a pressure regulating valve (10) for regulating the pressure in a high-pressure chamber (3) of a high-pressure accumulator (1), in particular of a high-pressure fuel accumulator. The pressure regulating valve (10) has a valve body (21), a valve seat (20) formed on the valve body, a valve pin (25) and a closing sleeve (30). At the closing sleeve (30) has a guide bore (31) is formed, which is longitudinally guided by the valve pin (25). The closure sleeve (30) cooperates with the valve seat (20) to open and close a hydraulic connection from the high pressure space (3) to a low pressure space (60). An actuator (45) acts on the closing sleeve (30) in the direction of the valve seat. Upstream of the valve seat (20), a valve space (27) of the valve body (21), the closing sleeve (30) and the valve pin (25) is limited. According to the invention, the diameter D _{20 of} the valve seat (20) is greater than the diameter D _{31 of} the guide bore (31).

Description

The present invention relates to a partial pressure compensated pressure regulating valve for controlling a pressure in a high pressure accumulator, and a high pressure accumulator having a pressure regulating valve.

State of the art

In modern diesel and gasoline engines today so-called storage injection systems are used, in which fuel is conveyed by a high-pressure pump in a high-pressure accumulator and is metered from this high pressure accumulator via injectors into the combustion chambers of an internal combustion engine. The high-pressure accumulator can be referred to, for example, as a fuel pressure accumulator or high-pressure fuel storage. For the injection of the fuel into the combustion chamber, the fuel from the high-pressure pump to up to 400 bar (gasoline engine) or 3000 bar and more (diesel engine) is compressed. The regulation of the pressure can be done via a pressure sensor and a pressure control valve, which are each mounted on the high-pressure accumulator. Such a high-pressure accumulator is from the DE 10 2008 040 901 known.

For the embodiments of the pressure control valves is known that pressure balanced control valves can be used as in the DE 10 2012 221 157 A1 disclosed. The term "pressure balanced" refers to the forces acting on the valve closing body or on the closing sleeve hydraulic forces; these cancel each other out in the closed valve state or almost on. Advantages of these valves are that comparatively small closing springs and actuators can be used, since it requires only very small forces to move the closing sleeve in the opening direction. However, it is very difficult to control an exact operating point or stroke in order to regulate the pressure in the high-pressure accumulator in pressure-balanced valves, especially at comparatively low strokes of the closing sleeve, due to the forces prevailing on the pressure-balanced locking sleeve force relationships.

Disclosure of the invention

The pressure control valve according to the invention for regulating the pressure in a high-pressure chamber of a high-pressure accumulator, in particular a high-pressure fuel accumulator has the advantage that it is not pressure-balanced but only partial pressure compensated, the term "partial pressure compensated" as "partially pressure balanced" or "partially force balanced" understand is. This creates a force acting on the closing sleeve in the opening direction hydraulic force, which reduces with increasing stroke of the closing sleeve. This hydraulic force is more reliable and robust controllable at small strokes than a spring force and also not proportional to the stroke of the closing sleeve. The overall control characteristic of the pressure control valve is thereby improved. At the same time, the energy requirement for the pressure regulating valve according to the invention is only insignificantly higher than for a pressure-balanced pressure regulating valve.

For this purpose, the pressure regulating valve comprises a valve body, a valve seat formed on the valve body, a valve pin and a closing sleeve. At the closing sleeve, a guide bore is formed, which is longitudinally guided by the valve pin. The closure sleeve cooperates with the valve seat to open and close a hydraulic connection from the high pressure space to a low pressure space. An actuator acts on the closing sleeve in the direction of the valve seat. Upstream of the valve seat, a valve space is defined by the valve body, the closure sleeve and the valve pin. According to the invention, the diameter D _{20 of} the valve seat is greater than the diameter D _{31 of} the guide bore.

By the valve spool effective for the opening hydraulic force surface of the closing sleeve is reduced, since the hydraulic forces absorbed by the valve pin do not act on the closing sleeve. Due to the diameter relationship D ₂₀ > D ₃₁ is still a - advantageously comparatively small - effective area on the closing sleeve left, so that there is a hydraulic opening force on the closing sleeve with a closed pressure control valve. The valve chamber is arranged in the direction of flow of the valve between the high-pressure chamber and the low-pressure chamber; the pressure in the valve chamber is the pressure relevant to the hydraulic force acting on the closing sleeve. Furthermore, a variable further force on the closing sleeve can be controlled by the actuator. The force-stroke curves of the hydraulic force and the actuator force have different gradients in the relevant operating points, so that these operating points can be set robust. This results in a very variable control characteristic for the pressure control valve.

In an advantageous embodiment of the pressure control valve, a valve bore defining the extended bore is then formed in the closing sleeve on the guide bore. The extended bore has an enlarged cross-section with respect to the guide bore. As a result, the area effective for the hydraulic pressure surface of the closing sleeve is increased.

Advantageously, the guide bore and the extended bore are designed as a stepped bore with a paragraph. Thus the Guide bore and the extended bore are very easy to manufacture.

In a development of the invention, the widened bore is designed as a conical surface widening toward the valve seat. By the cone effective for the hydraulic pressure surface of the closing sleeve is increased. In alternative embodiments, the shoulder of the guide bore can also be combined with the conical surface.

Advantageously, a connecting bore is formed in the valve body, which connects the high-pressure chamber with the valve chamber hydraulically. This communication hole defines a first constant throttle when the pressure control valve is open; When the closing sleeve is lifted, a second stroke-dependent throttle is created between the closing sleeve and the valve seat. By the ratio of the two throttles to each other, the pressure in the valve chamber is set and that variable between the high pressure in the high pressure chamber and the low pressure or atmospheric pressure in the low pressure space. The control characteristic of the pressure control valve is thus very variable and robust, since the pressure in the valve chamber can also be set very robust by the robustly set stroke of the closing sleeve.

In a further development of the invention, the valve pin is arranged on the valve body, that is formed integrally therewith. This reduces the number of components of the pressure regulating valve on the one hand. On the other hand, an outer surface of the valve pin, which is opposite to the guide bore and the valve seat formed on the same component, so that related tolerance errors are avoided.

Advantageously, in this case, the connection bore on a blind hole and at least one radial bore, wherein the radial bore connects the blind hole with the valve chamber. This results in a comparatively easy to manufacture T-shaped connecting bore, which can be on the axis of the valve body, so centrally formed. The arrangement of blind hole and radial bore (s), the flow can be influenced so advantageous that the hydraulic forces, especially lateral forces are minimized on the valve pin.

In an alternative advantageous embodiment, the pressure regulating valve has a valve housing, wherein the valve housing is clamped to the valve body. The valve pin is arranged at its end opposite the valve seat at least indirectly on the valve housing. As a result, the hydraulic forces acting on the valve pin are indirectly absorbed by the comparatively rigid valve housing. The "partial pressure compensation" of the pressure control valve is thus realized in a simple way.

Also in this embodiment, the connection bore may have a blind hole and at least one radial bore.

In an advantageous development of the valve pin is arranged with the interposition of a stop disc on the valve housing. By the stop disc, on which the valve pin preferably rests and does not strike, on the one tolerances can be compensated, on the other hand, a pressure and / or wear-resistant, different to the valve housing material can be used.

In advantageous embodiments, a spring acts at least indirectly on the closing sleeve in the opening direction. This can be advantageous in certain embodiments for the control of certain operating points, because thereby the operating points can be controlled even more robust. Furthermore, the spring is the reliable opening of the pressure control valve when the vehicle is parked. As a result, a negative pressure in the high-pressure accumulator is avoided by cooling fluid. In alternative embodiments, it is also possible to omit the spring completely and thus even more energy-efficient to control.

In advantageous embodiments, the actuator is designed as a magnetic actuator. Thus, the closing sleeve is electromagnetically controlled. This represents a simple and at the same time very accurate and robust control of the closing sleeve.

Advantageously, the maximum stroke of the closing sleeve is less than 100 microns. Especially with such small strokes a firmly defined and reproducible spring characteristic is hardly feasible. Therefore, it is especially in these strokes advantageous to minimize the interference from the spring to the closing sleeve (by reducing the spring stiffness) or completely eliminate (by omitting the spring). Such small strokes can be realized only by the partial pressure compensation, since thereby the diameter of the valve seat is increased. In order to open the required flow cross sections, a smaller stroke is therefore required in a partially pressure compensated valve than in a conventional valve, where correspondingly large strokes are used.

In advantageous embodiments, the pressure regulating valve is used in a high-pressure accumulator, in particular in a high-pressure fuel accumulator. In high-pressure accumulators, in particular in high-pressure fuel accumulators, very high pressures, in some cases more than 3000 bar, which, however, do not always have to be available, have an effect. The However, described embodiments of the pressure control valve according to the invention are suitable for such high demands. Furthermore, the pressure control valve according to the invention, however, can be controlled very quickly even with comparatively low energy, so that lower pressures can be set in the high-pressure accumulator.

drawings

Embodiments of the invention are illustrated in the following drawings and are explained in more detail in the following description.

1 shows a first embodiment with a high-pressure accumulator and a pressure control valve according to the invention, wherein only the essential areas are shown.

2 shows the section II of the 1 in a further embodiment.

3 shows a further embodiment of the pressure control valve according to the invention, wherein only the essential areas are shown.

4 shows a diagram with exemplary hydraulic forces and an actuator force on a closing member of the pressure regulating valve, wherein the forces are plotted against the stroke h of the closing member.

Description of the drawings

The invention and advantageous embodiments according to the features of the other claims are explained in more detail below with reference to the embodiments illustrated in the drawings.

In 1 is an area of high pressure storage 1 with a pressure control valve according to the invention 10 shown, with only the essential areas are shown. In the area not shown, the high-pressure accumulator 1 the known, usual connections on: one coming from a high-pressure pump high pressure port and at least one, but usually several injection injectors leading to injector connections.

• – Gehäuse 2 mit Innengewinde und Ventilgehäuse 12 mit Außengewinde,
• – Schraubverbindung mit einer zusätzlichen Spannmutter,
• – Pressverbindung zwischen Gehäuse 2 und Ventilgehäuse 12,
• – Schweißverbindung zwischen Gehäuse 2 und Ventilgehäuse 12.

The high-pressure accumulator 1 has a substantially cylindrical housing 2 on, which also has a substantially cylindrical high-pressure chamber 3 surrounds. On the case 2 is at an end area 7 an external thread 6 formed on the internal thread of a valve housing 12 the pressure control valve according to the invention 10 can be screwed. This connection between high-pressure accumulator 1 and pressure control valve 10 is chosen only by way of example and can be replaced by any other compounds, for example:

• - Casing 2 with internal thread and valve body 12 with external thread,
• - screw connection with an additional clamping nut,
• - Press connection between housing 2 and valve housing 12 .
• - Welded connection between housing 2 and valve housing 12 ,

In the embodiment of 1 is the valve body 12 executed in two parts, but may also be made in one piece in alternative embodiments. Furthermore, in alternative embodiments, the valve body 21 and the case 2 be made in one piece, so that the valve seat 20 at the high-pressure accumulator 1 is trained. The valve body 21 or the housing 2 would then be both part of the high-pressure accumulator 1 as well as the pressure control valve 10 , Will below the valve body 21 spoken, so this includes both the one-piece and the two-part design of valve body 21 and housing 2 unless otherwise stated.

The pressure control valve 10 has the valve body 12 , a valve body 21 , one on the valve body 21 trained valve seat 20 , a valve pin 25 and a closing sleeve 30 on. The locking sleeve 30 acts with the valve seat 20 together and thereby opens and closes a hydraulic connection from the high-pressure chamber 3 to a low-pressure room 60 , where the low pressure space 60 downstream of the valve seat 20 between valve housing 12 , Valve body 21 and closing sleeve 30 is trained. In the low pressure room 60 one opens in the valve housing 12 trained return bore 49 which in turn is advantageously connected to a return line, not shown.

The valve pin 25 supports itself with the interposition of a stop washer 28 on the valve body 12 on the valve body 21 away from the side. In the locking sleeve 30 is a guide bore in the longitudinal direction 31 formed, in which the valve pin 25 is arranged so that the closing sleeve 30 from the valve pin 25 is guided longitudinally movable. At the same time, the comparatively narrow guide gap between valve bolts 25 and guide bore 31 the high pressure area sealed; Naturally, this seal is carried out under a minimum leakage through the guide gap. The locking sleeve 30 in turn is in a valve housing 12 arranged guide sleeve 48 guided longitudinally movable. Here is the guide sleeve 48 designed to provide the hydraulic connection from the low pressure space 60 to the return bore 49 does not close. Furthermore, the guide sleeve 49 be executed so that they have a Fluid exchange between the low pressure space 60 and the low pressure area at the valve seat 20 opposite end of the valve pin 25 allows; This can be done, for example, by a triflate on the outer surface of the guide sleeve 49 respectively.

Upstream of the valve seat 20 is between the valve body 21 , the closing sleeve 30 and the valve pin 25 a valve room 27 educated. In the valve body 21 is a connection hole 22 formed the the high pressure room 3 with the valve room 27 connects hydraulically. In this case, the connection hole 22 also have a defined throttle point. With closed pressure control valve 10 So if the locking sleeve 30 at the valve seat 20 is applied, is a hydraulic connection between the valve chamber 27 and the low-pressure room 60 closed; the valve room 27 then has the same pressure as the high-pressure chamber 3 , With pressure control valve open 10 So if the locking sleeve 30 from the valve seat 20 is lifted, is the hydraulic connection between the valve chamber 27 and the low-pressure room 60 open; the valve room 27 then has a pressure between that of the high-pressure chamber 3 and that of the low pressure space 60 lies.

In a high-pressure accumulator 1 remote area of the pressure control valve 10 is an actor 45 in the valve housing 12 arranged to the closing member 30 to press. In the embodiment of 1 is the actor 45 designed as a magnetic actuator; In general, however, any actuator, for example a piezoelectric actuator or a pneumatic actuator, can be used for the present invention. For opening and closing the closing element 30 is on the closing link 30 in the case of a magnetic actuator 45 a magnet armature 42 arranged, for example, pressed on. The magnetic actuator 45 is between the magnet armature 42 and the valve seat 20 arranged. The magnet armature 42 is thus when energizing the Magnetaktors 45 from this in the direction of the valve seat 20 tightened so that the magnet armature 42 and with it the closing element 30 in the direction of the valve seat 20 emotional. Between the magnet armature 42 and the valve seat 20 is a spring 47 arranged, which with the closing member 30 connected armature 42 against the force of the magnetic actuator 45 returns to its original position. One speaks therefore of a normally open pressure control valve 10 ,

In the embodiment of 1 is at the high-pressure accumulator 1 opposite end of the pressure control valve 10 a stop plate 29 in the valve housing 12 arranged. The stop plate 29 limits a maximum stroke of the armature 42 and thus the closing sleeve 30 in the opened state of the pressure regulating valve 10 , In the closed state advantageously remains a gap between the magnetic actuator 45 and magnet armature 42 to avoid "sticking" of the two parts. In alternative embodiments, this can also be achieved by a residual air gap disk between the magnetic actuator 45 and magnet armature 42 respectively.

According to the invention, the pressure regulating valve 10 Partially balanced in the closed state. In the embodiment of 1 this is through a paragraph 32 the closing sleeve 30 realized, the paragraph 32 an extended hole 33 having. The valve pin 25 partially protrudes into the extended bore 33 into it, leaving the valve room 27 also on the volume between extended bore 33 and valve pin 25 extends. The locking sleeve 30 owns in the guide hole 31 the diameter D ₃₁ . In the area of the valve chamber 27 So, at the heel 32 owns the extended bore 33 the diameter D ₃₃ .

In the embodiment of 1 is the extended hole 33 Cylindrical, so that the diameter D _{33 of} the extended bore 33 equal to the diameter D _{20 of} the valve seat 20 is. For the partial pressure compensated pressure control valve according to the invention 10 of the embodiment of 1 applies: D ₃₃ = D ₂₀ and D ₃₃ > D ₃₁ .

2 shows the section II of the 1 in the area of the valve chamber 27 in a further embodiment. The locking sleeve 30 This embodiment has instead of a paragraph one of the guide bore 31 to the valve seat 20 expanding conical surface 34 on. The extended bore 33 is therefore not cylindrical, but as a conical surface 34 , The other illustrated components are substantially similar to the embodiment of 1 designed.

3 shows a further embodiment of the pressure control valve according to the invention 10 , where only the essential areas are shown. The to 1 analogously constructed areas have already been described in the description of 1 explained and will not be repeated here, it is only on the differences to 1 To be received.

The embodiment of 3 shows an actuator designed as a magnetic actuator 45 that the magnet armature 42 is arranged radially surrounding. In this case, the magnetic actuator 45 , as in 3 shown outside the valve body 12 be arranged, or in alternative embodiments, the valve housing 12 designed accordingly, that also the magnetic actuator 45 in the valve housing 12 is arranged. In the valve housing 12 is between the magnetic actuator 45 and the armature 42 an amagnetic region 44 arranged so that when energizing the actuator 45 a magnetic force on the armature 42 in the direction of the valve seat 20 acts.

The valve pin 25 is in the embodiment of 3 on the valve body 21 arranged or designed in one piece with this. The connection hole 22 is characterized T-shaped and includes a blind hole 22a and at least one radial bore 22b , The blind hole 22a leads from the high-pressure chamber, not shown 3 in the axial direction into the interior of the valve body 21 and cuts there with the at least one radial bore 22b which leads away radially outwards and into the valve chamber 27 empties. Advantageously, two to four radial bores 22b formed star-shaped leading outward. The actual throttle point of the connection bore 22 can do both in the blind hole 22a as well as in the at least one radial bore 22b be educated.

In the embodiment of 3 is the locking sleeve 30 with paragraph 32 and extended bore 33 educated. However, any other design is possible as long as the diameter D _{31 of} the guide bore 31 smaller than the diameter D _{20 of} the valve seat 20 ,

4 shows a diagram with three curves 101 . 102 . 103 , and an operating point 104 , wherein the force F over the stroke h of the closing member 30 is applied. A stroke h = 0 corresponds to the closed pressure control valve 10 So one on the valve seat 20 adjacent closing sleeve 30 , The first turn 101 shows the course of the actuator force, such as a magnetic force between magnetic actuator 45 and magnet armature 42 that is about the connection of magnet armature 42 to the closing sleeve 30 on the locking sleeve 30 acts. With increasing distance from armature 42 to magnetic actuator 45 , ie with increasing stroke h, this actuator force decreases.

The second turn 102 shows the hydraulic force on the closing member 30 a pressure balanced pressure control valve 10 , wherein the hydraulic power is very low and is relatively strongly influenced by the flow conditions. In this case, it is necessary the closing member 30 through the use of a strong spring 47 to balance.

The third turn 103 shows the hydraulic force on the closing member 30 the partial pressure compensated pressure control valve according to the invention 10 , wherein the hydraulic force in the opposite direction to the actuator force of the first curve 101 acts. Due to the diameter relationship D ₂₀ > D ₃₁ is in this case, the hydraulic force on the closing member 30 for the closed pressure control valve 10 greater than in the case of a pressure compensated pressure control valve. At the operating point 104 there is balance between the hydraulic and the actuator force; the closing sleeve 30 is in the associated stroke h ₁ thus in the balance of power. The use of a on the closing member 30 acting spring 47 This can even be eliminated. The greater the angle α between the hydraulic and the actuator force at the operating point 104 is, the more reliable and robust, the associated stroke h _{1 can be} controlled. The control of the operating point 104 different operating points then takes place by changing the actuator force, so for example by changing the current in the solenoid actuator 45 ,

The operation of the pressure control valve according to the invention 10 is as follows:
In the initial state is the pressure control valve 10 energized, giving a force through the actuator 45 is generated, for example, a magnetic force on the armature 42 acts. By the magnetic force of the armature 42 in the direction of the valve seat 20 moves and with it the closing element 30 against the valve seat 20 pressed, so that a fluidic or hydraulic connection from the high-pressure chamber 3 over the connecting hole 22 , the valve seat 20 and the valve room 27 to the low-pressure room 60 is interrupted. Is the current to the actuator 45 interrupted, so press the spring 47 and the hydraulic force on the closing member 30 the closing member 30 towards the valve seat 20 , where the spring 47 only optional. The pressure control valve 10 is thereby opened, which opens the fluidic connection described and a pressure reduction in the high-pressure chamber 3 is possible.

The valve pin 25 does the job on the lock sleeve 30 to reduce acting hydraulic forces, as the high pressure between the guide bore 31 and the valve piston 25 from the valve room 27 up to the valve seat 20 opposite end of the closing sleeve 30 is reduced. Is the diameter D _{31 of} the guide bore 31 equal to the diameter D _{20 of} the valve seat, so is the closing sleeve 30 pressure-balanced. According to the invention, the diameter D _{31 of} the guide bore 31 however smaller than the diameter D _{20 of} the valve seat, leaving an opening hydraulic force on the closing sleeve 30 acts when the valve space 27 is under high pressure, so if the locking sleeve 30 the fluidic or hydraulic connection from the valve chamber 27 to the low-pressure room 60 by contact with the valve seat 20 closes.

This can, as in 4 shown a stable balance between the on the closing sleeve 30 acting forces - actuator force, hydraulic force and optional spring force - can be achieved. The controlled for most operating strokes h of the closing sleeve 30 are in the range of 30 microns to 50 microns. It is difficult to achieve a proportional one over this comparatively short distance, especially in mass production and robust spring characteristic for the spring 47 to realize. For the pressure control valve according to the invention 10 can the spring force of the spring 47 be chosen comparatively low or the spring 47 even be omitted altogether, so that the potential for interference by the spring 47 significantly reduced or completely eliminated. This allows individual operating points of the pressure control valve 10 through different operating points and in the high pressure room 3 ruling pressures assigned to the current of the actuator 45 be controlled robust and reliable.

• • Die Abstimmung von zwei Drosselwirkungen aufeinander: eine erste konstante Drossel, die Verbindungsbohrung 22, und eine zweite variable Drossel, nämlich die Drossel bei vom Ventilsitz 20 abgehobener Schließhülse 30, die sich dann zwischen Ventilsitz 20 und Schließhülse 30 ergibt. Dadurch wird der Druck im Ventilraum 27 in Abhängigkeit des Hubs h der Schließhülse 30 und in Abhängigkeit des im Hochdruckraum 3 herrschenden Drucks eingestellt.
• • Die für die hydraulisch öffnende Kraft wirksame Fläche der Schließhülse 30, die sich durch die Differenz der beiden Durchmesser D₂₀ und D₃₁ ergibt. Aus dem Produkt dieser wirksamen Fläche mit dem im Ventilraum 27 herrschenden Druck ergibt sich die auf die Schließhülse 30 wirkende hydraulische Kraft.

The performance of the control of the operating points is influenced constructively by the following factors:

• • The tuning of two throttle effects on each other: a first constant throttle, the connection hole 22 , And a second variable throttle, namely the throttle from the valve seat 20 lifted lock sleeve 30 , which is then between valve seat 20 and closing sleeve 30 results. This will cause the pressure in the valve chamber 27 depending on the stroke h of the closing sleeve 30 and depending on the in the high pressure room 3 adjusted pressure.
• • The area of the closing sleeve effective for the hydraulic opening force 30 , which results from the difference between the two diameters D ₂₀ and D ₃₁ . From the product of this effective area with the one in the valve room 27 prevailing pressure results on the closing sleeve 30 acting hydraulic force.

QUOTES INCLUDE IN THE DESCRIPTION

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

Cited patent literature

• DE 102008040901 [0002]
• DE 102012221157 A1 [0003]

Claims (13)

Pressure control valve ( 10 ) for regulating the pressure in a high-pressure chamber ( 3 ) of a high-pressure accumulator ( 1 ), in particular a fuel high-pressure accumulator, wherein the pressure regulating valve ( 10 ) a valve body ( 21 ), one on the valve body ( 21 ) formed valve seat ( 20 ), a valve pin ( 25 ) and a closing sleeve ( 30 ), wherein at the closing sleeve ( 30 ) a guide bore ( 31 ) formed by the valve pin ( 25 ) is longitudinally guided, wherein the closing sleeve ( 30 ) with the valve seat ( 20 ) cooperates to a hydraulic connection from the high-pressure chamber ( 3 ) to a low pressure space ( 60 ) to open and close, with an actuator ( 45 ) on the closing sleeve ( 30 ) acts in the direction of the valve seat, wherein upstream of the valve seat ( 20 ) a valve space ( 27 ) of the valve body ( 21 ), the closing sleeve ( 30 ) and the valve pin ( 25 ) is limited, characterized in that the diameter D _{20 of} the valve seat ( 20 ) is greater than the diameter D _{31 of} the guide bore ( 31 ). Pressure control valve ( 10 ) according to claim 1, characterized in that in the closing sleeve ( 30 ) to the guide bore ( 31 ) then a valve space ( 27 ) limiting extended bore ( 33 ) is trained. Pressure control valve ( 10 ) according to claim 2, characterized in that the guide bore ( 31 ) and the extended bore ( 33 ) as a stepped bore with a paragraph ( 32 ) are executed. Pressure control valve ( 10 ) according to claim 2 or 3, characterized in that the enlarged bore ( 33 ) as one to the valve seat ( 20 ) expanding conical surface ( 34 ) is trained. Pressure control valve ( 10 ) according to one of claims 1 to 4, characterized in that in the valve body ( 21 ) a connection hole ( 22 ) is formed, which the high pressure space ( 3 ) with the valve space ( 27 ) connects. Pressure control valve ( 10 ) according to claim 5, characterized in that the connecting bore ( 22 ) a blind hole ( 22a ) and at least one radial bore ( 22b ), wherein the radial bore ( 22b ) the blind hole ( 22a ) with the valve space ( 27 ) connects. Pressure control valve ( 10 ) according to one of claims 1 to 6, characterized in that the valve pin ( 25 ) on the valve body ( 21 ) is arranged. Pressure control valve ( 10 ) according to one of claims 1 to 6, characterized in that the pressure regulating valve ( 10 ) a valve housing ( 12 ), wherein the valve housing ( 12 ) with the valve body ( 21 ) and wherein the valve pin ( 25 ) at its the valve seat ( 20 ) opposite end at least indirectly on the valve housing ( 12 ) is arranged. Pressure control valve ( 10 ) according to claim 8, characterized in that the valve pin ( 25 ) with the interposition of a stop disc ( 28 ) on the valve housing ( 12 ) is arranged. Pressure control valve ( 10 ) according to one of claims 1 to 9, characterized in that a spring ( 47 ) at least indirectly on the closure sleeve ( 30 ) acts in the opening direction. Pressure control valve ( 10 ) according to one of claims 1 to 10, characterized in that the actuator ( 45 ) is designed as a magnetic actuator. Pressure control valve ( 10 ) according to one of claims 1 to 11, characterized in that the maximum stroke of the closing sleeve ( 30 ) is smaller than 100 μm. High-pressure accumulator ( 1 ) with a high-pressure chamber ( 3 ) and a pressure regulating valve ( 10 ) according to claims 1 to 12.

Images