A pressure-regulating valve for a fluid medium that is at system pressure, e.g., for system pressures >1000 bar, has a valve housing with an inlet channel and at least one outlet channel. A valve seat arranged in the valve housing has a conical recess holding an axially mobile valve body with a lateral outer surface at least part of which is conical. The interaction of the valve body and valve seat regulate throughflow of medium from the inlet channel to the outlet channel. The valve seat, adjacent to the lateral outer surface of the valve body, includes a first pressure chamber from which there extends, in the direction of movement of the valve body, a throttle gap along the lateral outer surface of the valve body. The conical lateral outer surface of the valve body extends, in the direction of movement of the valve body, on either side of the pressure chamber through the conical recess of the valve seat.

BACKGROUND AND SUMMARY OF THE INVENTION

Exemplary embodiments of the present invention relate to a pressure regulating valve.

A generic pressure regulating valve is known, for example, from EP 1 450 082 B1.

Such pressure regulating valves are used in high-pressure technology to mitigate pressure fluctuations in high-pressure systems caused, for example, as a result of high-pressure consumers, such as high-pressure spray guns, being switched on or off. Furthermore, such pressure regulating valves are used to control the pressure, for example to control a pressure build-up or pressure reduction with a predetermined pressure gradient.

In addition to their use in high-pressure technology, such pressure regulating valves can also be used, for example, to homogenize media in process engineering. In this application, a homogenization of the medium conveyed through the pressure regulating valve is effected within the throttle range of such a pressure regulating valve, i.e., the viscosity or consistency of the same is influenced.

Such a pressure regulating valve usually has a valve housing having an inlet channel and at least one outlet channel for the passage of a fluid medium under system pressure. A valve seat is arranged in the valve housing, in which a valve body, which can also be referred to as a control in, is mounted in an axially movable manner and can be adjusted in the valve seat with the aid of an actuating unit in such a way that, as a result of an increase in the system pressure, the valve body is moved out of the valve seat to such an extent that a corresponding quantity of the fluid medium can flow out via the pressure regulating valve until the system pressure is reduced again to the predetermined level.

One problem with pressure regulating valves known from the prior art, especially those used in ultrahigh pressure technology of over 500 bar, is the large adjustment forces required to actuate the valve body under operating conditions. These large adjustment forces result in this case from the applied operating pressure and the pressurized projected area of the valve body in the adjustment direction.

Exemplary embodiments of the present invention are directed to a pressure regulating valve whose valve body can be controlled or moved with significantly lower adjustment forces and which, in addition, can dispense with the use of wear-prone dynamic high-pressure contact seals.

The pressure regulating valve according to the invention for a fluid medium under system pressure, preferably for system pressures above 500 bar, has a valve housing in which an inlet channel and at least one outlet channel communicating therewith for the medium are provided.

The pressure regulating valve also has a valve seat arranged in the valve housing with a conically shaped receptacle in which an axially movable valve body having an at least partially conically shaped lateral outer surface is mounted. An actuating unit is in operative connection with the valve body.

A throughflow of medium from the inlet channel to the at least one outlet channel can be regulated in this case by the valve body in interaction with the valve seat.

In the valve seat, a first pressure chamber is provided adjacent to the lateral outer surface of the valve body, from which a throttle gap extends in each case along the lateral outer surface of the valve body in the direction of movement of the valve body.

The conically shaped lateral outer surface of the valve body extends in this case in the direction of movement of the valve body on both sides of the pressure chamber through the correspondingly conically shaped receptacle of the valve seat.

In the pressure regulating valve according to the invention, throttling areas provided on both sides of the first pressure chamber and formed by respective throttle gaps between the lateral outer surface of the valve body and the inner surface of the valve seat enable the high-pressure medium, which has entered through the inlet, to be reduced by being discharged via the two throttle gaps.

The medium under high pressure always moves along the lateral outer surface of the valve body and thus enables the valve body to be adjusted with significantly less force since, due to the conicity of the valve body, only a fraction of the force acting on the valve body by the high pressure medium acts in the axial or adjustment direction of the valve body.

According to an advantageous embodiment variant of the invention, a second pressure chamber is formed in a region of the inner circumference of the valve housing adjacent to the valve seat, radially outside the first pressure chamber, into which the inlet channel opens.

Through this second pressure chamber, the applied operating pressure of the fluid medium also acts on the outer jacket of the valve seat, thus reducing deformation-induced widening of the throttle gap as a result of the above-mentioned high pressures.

The first pressure chamber and the second pressure chamber are preferably annular.

According to a preferred embodiment variant of the pressure regulating valve according to the invention, the valve seat is installed in a receptacle of the valve housing in such a way that it cannot move. Alternatively, the valve seat can also be designed as a component of the valve housing.

According to a preferred embodiment variant of the pressure regulating valve according to the invention, the actuating unit can be controlled via a control unit measuring a system pressure, wherein the valve body can be moved into a position enlarging or reducing the throttle gaps depending on the measured system pressure.

According to an alternative embodiment variant, the actuating unit is designed as a force-regulated control unit, wherein the valve body can be moved into a position enlarging or reducing the throttle gaps against the preset force of a force accumulator corresponding to a set pressure, depending on the applied system pressure.

This variant has the advantage of self-regulation of the pressure regulating valve, where only the force of the force accumulator acting on the actuating body needs to be adjusted.

According to a preferred embodiment variant of the pressure regulating valve, a diameter of the conically shaped receptacle and the part of the valve body formed with a conically shaped lateral outer surface is designed to increase towards the actuating unit.

According to an alternative embodiment variant, the diameter of the conically shaped receptacle and the part of the valve body with a conically shaped lateral outer surface is designed to decrease towards the actuating unit.

According to another advantageous embodiment variant of the invention, the valve seat has a plurality of pressure chamber inlet channels extending tangentially from the first pressure chamber to the second pressure chamber.

With such a variant, lateral flow forces on the valve body in the first pressure chamber can be avoided.

According to a further advantageous embodiment variant of the invention, a plurality of grooves is preferably formed on the conically shaped lateral outer surface of the valve body.

These grooves are preferably formed in the lateral outer surface of the valve body along a plane perpendicular to the direction of movement of the valve body. It is also conceivable to form such grooves in the conically shaped inner surface of the valve seat.

By forming such grooves, the homogenization result is positively influenced in case the pressure regulating valve is used for homogenization of media.

According to a preferred embodiment variant, the valve body and the valve seat are made of a hardened steel, hard metal, or ceramic.

According to another alternative embodiment variant of a pressure regulating valve according to the invention for a fluid medium under system pressure, preferably for system pressures >500 bar, the pressure regulating valve has a valve housing in which at least one outlet channel for the medium is provided.

In the valve housing, a valve seat arranged along a displacement axis is provided with an at least partially conically shaped receptacle in which a valve body fixed to the valve housing is mounted with an at least partially conically shaped lateral outer surface and an inlet channel.

The pressure regulating valve also has an actuating unit that is operatively connected to the valve seat.

A throughflow of medium from the inlet channel to the at least one outlet channel can also be regulated in this variant by the valve seat in interaction with the valve body.

A pressure chamber is provided in the valve seat adjacent to the lateral outer surface of the valve body, from which a throttle gap extends in each case along the lateral outer surface of the valve body in the direction of movement of the valve seat, wherein the conically shaped lateral outer surface of the valve body extends on both sides of the pressure chamber through the correspondingly conically shaped receptacle of the valve seat in the direction of movement of the valve seat.

In this embodiment variant, too, the medium under high pressure always moves along the lateral outer surface of the valve body and thus enables the valve seat to be adjusted with significantly less force since, due to the conicity of the valve body and the valve seat, only a fraction of the force acting on the valve seat by the high-pressure medium acts in the axial or adjustment direction of the valve seat.

According to an advantageous further development of this embodiment variant, the inlet channel extends in the direction of movement of the valve seat.

The valve body preferably has a plurality of pressure chamber inlet channels extending radially from the inlet channel into the pressure chamber.

The radial width of the pressure chamber preferably corresponds to the width of the throttle gaps.

In this case, the receptacle is preferably of pot-shaped design, having an outlet channel in the bottom of the receptacle that opens into a low-pressure chamber of the valve housing.

DETAILED DESCRIPTION

In the following figure description, terms such as top, bottom, left, right, front, rear, etc. refer exclusively to the exemplary representation and position of the pressure regulating valve, valve housing, valve body, valve seat, pressure chamber and the like selected in the respective figures. These terms are not to be understood restrictively, i.e., due to different working positions or the mirror-symmetrical design or the like, these references may change.

InFIGS.1to3, the reference sign1is used to designate all in all one embodiment variant of a pressure regulating valve according to the invention.

As can be seen in particular inFIGS.2and3, the pressure regulating valve1has a valve housing2. The valve housing2has an inlet channel21and at least one outlet channel22,23communicating with the inlet channel21, through which a fluid medium under a system pressure can flow.

A valve seat4is arranged in the valve housing2. This valve seat4has a conically shaped receptacle42in which an axially movable valve body3having an at least partially conically shaped lateral outer surface33is mounted.

In the embodiment variant shown in the figures, the valve seat4is installed in a receptacle of the valve housing2in such a way that it cannot move.

However, it is also conceivable to form the valve seat4as a component of the valve housing2or to keep the valve body130immovable and the valve seat140movable, as explained below with reference toFIGS.8to10.

In addition to the conically shaped section31, the valve body3has a head32extending from the latter in the direction of its longitudinal axis L in the direction of movement x, which head32is guided in a preferably cylindrical receptacle of a guide housing6so as to be movable in translation in the direction of the longitudinal axis L.

This guide housing6also holds a pressure piston10, which is coupled to an actuating unit5that is used to set a predetermined back pressure and thus to regulate the system pressure to a predetermined value.

This actuating unit5is operatively connected with the valve body3, here via the pressure piston10.

A through-flow of the pressurized fluid medium from the inlet channel21to the at least one outlet channel22,23can be regulated in this case by the valve body3in interaction with the valve seat4.

For this purpose, a first pressure chamber7is provided in the valve seat4, adjacent to the lateral outer surface33of the valve body3, from which a throttle gap8extends in each case along the lateral outer surface33of the valve body3in the direction of movement of the valve body3along the longitudinal axis L.

As can be seen inFIGS.2-5, the conically shaped lateral outer surface33of the valve body3extends in this case in the direction of movement of the valve body3on both sides of the pressure chamber7through the correspondingly conically shaped receptacle42of the valve seat4.

FIG.4shows a position of the valve body3in the valve seat4, in which a very small gap8remains between the lateral outer surface33of the valve body3and the inner surface of the valve seat4, through which correspondingly only a small volume of the pressurized medium is able to flow in a predetermined time.

If the system pressure rises, for example as a result of a high-pressure consumer in the high-pressure system in which the pressure regulating valve1is installed being switched off, this leads to a pressure increase in the first pressure chamber7, whereupon a force is exerted on the valve body3on the basis of the proportional force vector in the direction L of the longitudinal axis in the direction of increasing cross-section of the valve body3, thus moving the valve body3further into the position shown by way of example inFIG.5, which leads to a widening of the throttle gap8and thus allows a larger volume flow.

Since a range of the high pressure applied in the pressure chamber7causes the fluid under high pressure to act exclusively on the lateral outer surface33of the valve body3, the force acting on the valve body3in the direction of the longitudinal axis L is significantly reduced compared to an arrangement known from the prior art in which the high pressure also acts on at least one end face of such a valve body3.

In this context, the end face of a valve body is to be understood as a surface aligned perpendicularly to the direction of movement, on which the force of a fluid under high pressure acts. The term “end face” should not be understood to mean, for example, the face of a groove aligned perpendicularly to the direction of movement, in which the fluid under high pressure acts against both opposite perpendicular faces of the same body, so that the forces acting on these faces cancel each other out.

As can be seen in particular inFIG.3, in the preferred embodiment variant shown here, a second pressure chamber24is integrally formed radially outside the first pressure chamber7in a region of the inner circumference of the valve housing2adjacent to the valve seat4, into which the inlet channel21opens.

The arrangement of this second pressure chamber24radially to the first pressure chamber7effectively prevents deformation of the valve seat4.

Both the first pressure chamber7and the second pressure chamber24are preferably annular in shape, as can be seen for example inFIG.2.

The first pressure chamber7does not necessarily have to be formed as material recess of the valve seat4in this case, as shown inFIG.3. It is also conceivable to design the first pressure chamber7as a connecting or continuation piece of the two throttle gaps8, i.e., without a material recess on the valve seat4, so that the first pressure chamber7is defined by the inlet of a pressure chamber inlet channel41of the valve seat4into the cavity of the valve seat4accommodating the valve body3.

As further shown inFIGS.2and3, the valve seat4, which is designed here as a separate component, is sealed radially outside towards the valve housing2by static high-pressure seals9.

The head32of the valve body3is sealed towards the inner surface of the guide housing6by means of dynamic low-pressure seals12, since in this area the medium under high pressure applied at the inlet channel21has already passed through the throttle gaps8, wherein outside the valve seat4in the transition area to the head32of the valve body3there is a connection to the outlet channel22of the housing. For this purpose, a receiving groove35for the low-pressure seal is provided in the region of the head32.

Instead of the two outlet channels22,23shown here inFIGS.2and3, it is also conceivable to have them open into a single outlet channel via corresponding through-holes in the housing2.

The housing2is also sealed by a low-pressure seal11in connection with the cylindrical receptacle62of the guide housing6.

While in the embodiment variants shown in the figures the diameter of the conically shaped receptacle42and of the part of the valve body3formed with a conically shaped lateral outer surface33is designed to increase towards the actuating unit5, in an alternative embodiment variant (not shown here) it is also conceivable that the diameter of the conically shaped receptacle42and of the part of the valve body3formed with a conically shaped lateral outer surface33is designed to decrease towards the actuating unit5.

For the latter of the two embodiment variants, an actuating unit5is required which can be controlled via a control unit measuring a system pressure, wherein the valve body3can be moved into a position enlarging or reducing the throttle gaps8depending on the measured system pressure.

Such directional control can be achieved, for example, by means of an electrically actuated lifting cylinder, in which the pressure piston10shown in the figures is firmly connected to the valve body3and is thus capable of exerting both a tensile and a compressive force on the valve body3.

In the first-mentioned embodiment variant of the alignment of the conicity of the valve body3and the valve seat4, in which a diameter of the conically shaped receptacle42and of the part of the valve body3formed with a conically shaped lateral outer surface33is designed to increase towards the actuating unit5, on the other hand, the pressure piston10can also be mounted in such a way that it is capable of exerting only a pressure force on the valve body3.

Furthermore, in this embodiment variant it is also possible to design the actuating unit5as a force-regulated control unit, in which the valve body3can be moved into a position enlarging or reducing the throttle gaps8against the preset force of a force accumulator corresponding to a set pressure, depending on the applied system pressure.

In this case, the force accumulator can be an adjustable spring or a pneumatic cylinder that can be set to as specified set pressure.

If the volume flow increases via the inlet channel21, this leads to an increase in pressure in the high-pressure area of the pressure regulating valve1. This causes the throttle gaps8between the valve body3and the valve seat4to widen until the pressure set in the high-pressure area has dropped to the preset system pressure and, accordingly, the hydraulic pressure of the medium applied in the area of the inlet channel21is in force equilibrium with the pneumatic cylinder.

As can be seen inFIG.6, the valve seat4has a plurality of pressure chamber inlet channels41extending tangentially from the first pressure chamber7to the second pressure chamber24.

The advantage of such a tangential connection, in contrast to a radial inlet of such a pressure chamber inlet channel41, is the prevention of transverse flow forces in the first pressure chamber7.

As shown in the alternative embodiment variant of the pressure regulating valve1illustrated inFIG.7, here the conically shaped section31of the valve body3has a plurality of grooves34formed in the lateral outer surface33of the valve body3.

In this case, the grooves34are preferably formed in the lateral outer surface33of the valve body3along a plane perpendicular to the direction of movement of the valve body3. By forming such grooves34, the homogenization result is positively influenced when using the pressure regulating valve1for homogenizing media.

Hard materials such as hardened steel, hard metal, or even ceramics are preferably used as material for the valve body3and the valve seat4.

A further alternative embodiment variant of a pressure regulating valve100according to the invention is described below with reference toFIGS.8to10.

This pressure regulating valve100for a fluid medium under system pressure, preferably for system pressures greater than 500 bar, also has a valve housing120in which at least one outlet channel122,123is provided for the medium.

As further shown inFIGS.9and10, the pressure regulating valve100comprises a valve seat140arranged in the valve housing120along a displacement axis L and having an at least partially conically shaped receptacle142in which a valve body130fixed to the valve housing120and having an at least partially conically shaped lateral outer surface133and an inlet channel134is supported.

Accordingly, in this embodiment variant, the valve seat140is the moving part and not the valve body130, in contrast to the embodiment variants described with reference toFIGS.1to7.

Here, an actuating unit110is in operative connection with the valve seat140.

A medium flow from the inlet channel134to the at least one outlet channel122,123can also be regulated here by the valve seat140in interaction with the valve body130.

Here, too, a pressure chamber170is provided in the valve seat140adjacent to the lateral outer surface133of the valve body130, from each of which a throttle gap180extends along the lateral outer surface133of the valve body130in the direction of movement of the valve seat140.

Likewise, the conically shaped lateral outer surface133of the valve body130extends in the direction of movement of the valve seat140on both sides of the pressure chamber170through the correspondingly conically shaped receptacle142of the valve seat140.

As further shown inFIGS.8to10, a neck132of the valve body130extends through an opening125of the valve housing120and is secured to the valve housing120outside the valve housing120by a fastening element121.

The fastening element121is preferably formed as a nut, which is screwed onto an external thread of the neck132of the valve body130.

In a low-pressure chamber124of the valve housing120, the neck132expands to such an extent that it abuts an inner wall of the low-pressure chamber124with a counter step136and is thus fixed to the valve housing120with the aid of the fastening element121, which is formed as a nut.

However, other possible ways of fixing the valve body130to the valve housing120are also conceivable.

A static low-pressure seal111is inserted in the area of the opening125for fluidic sealing.

The conical section132of the valve body130then adjoins the part of the neck132of the valve body130that has been widened by the step136, and its lateral outer surface133, together with the lateral inner surface of the receptacle142of the valve seat140, forms the throttle gaps180.

The inlet channel134extends centrally from a connecting piece outside the valve housing120through the neck132of the valve body130to the region of the conical section131. From there a plurality of pressure chamber inlet channels135preferably extends to the lateral outer surface133of the valve body130to form the pressure chamber170in this region.

As can be further seen inFIGS.9and10, the radial width of the pressure chamber170preferably corresponds to the width of the throttle gaps180.

An embodiment variant similar to that shown inFIG.3is also conceivable here, with material recesses in the area of the orifice of the pressure chamber inlet channels135on the lateral outer surface133of the valve body3.

Preferably, the pressure chamber inlet channels135extend perpendicularly to the lateral outer surface133of the valve body130in this case.

When pressurized, a force acts on the valve seat140due to the proportional force vector in the direction L of the longitudinal axis of the valve seat140, in the direction of increasing cross-section of the valve seat4.

The valve seat4is moved in this case from the position shown inFIG.9to the position shown inFIG.10, resulting in a widening of the throttle gaps180and thus allowing a larger volume flow.

As further shown inFIGS.9and10, the receptacle142of the valve seat140is pot-shaped having an outlet channel143in the bottom of the receptacle142opening into a low-pressure chamber124of the valve housing120, through which a portion of the fluid medium can further flow out via the outlet channel143of the valve seat140through the outlet122of the valve horsing120after passing through the throttle gap180on the left inFIGS.9and10.

A further portion of the fluid medium can flow out via the low-pressure chamber124and the outlet123in the valve housing120after passing through the throttle gap180on the right inFIGS.9and10.

The actuating unit110shown by way of example inFIGS.9and10preferably corresponds in this case to the embodiment variant shown inFIGS.2and3, in the form of a pressure piston that is held on the guide housing160and can be set to a predetermined counterpressure by an actuating element and thus serves to regulate the system pressure to a predetermined value.

The guide housing160is also preferably connected here to the valve housing120with the aid of fixing screws162.

A valve seat receptacle163is provided centrally in the guide housing160, in which a head144of the valve seat140is accommodated so as to be displaceable in the L direction.

A groove is provided at the head144of the valve seat140to fluidically seal the valve seat140to the guide housing160, in which groove a dynamic low-pressure seal112is accommodated.

LIST OF REFERENCE SIGNS