DE102016122506A1 - Flow control valve and hydraulic system - Google Patents

Abstract

A flow restriction valve (10) having a cage (12) insertable into a fluid channel (18) and having a first axial end (22) and a second axial end (24), and a locking member (14) attached to the first Cage (12) between a locking position (SP) and a release position (FP) is movable, wherein the cage (12) is formed so that in the release position (FP) of the locking element (14) the first and the second axial end (22 , 24) are interconnected via a first passage (26) and a second passage (28), the first passage (26) defining a first flow area (A1), the second passage (28) defining a second flow area (A2) and wherein the cage (12) is further formed such that in the locking position (SP) of the locking element (14) the first axial end (22) and the second axial end (24) are interconnected only via the second passage (28) are. In this case, the second passage (28) is formed by a single channel. ( 1 )

Description

The present invention relates to a flow restriction valve having a cage which is insertable into a fluid channel and which has a first axial end and a second axial end, and with a locking element which is movable on the cage between a locking position and a release position, wherein the cage is formed such that in the release position of the blocking element, the first and the second axial end via a first passage and a second passage are interconnected, wherein the first passage defines a first flow area, wherein the second passage defines a second flow area, and wherein the Cage is further formed so that in the locking position of the locking element, the first axial end and the second axial end are interconnected only via the second passage.

Furthermore, the present invention relates to a hydraulic arrangement with a fluid supply device, with a hydraulic consumer and with a flow-limiting valve of the type specified above.

Flow control valves are passive valves that are controlled and switched solely on the basis of the pressure conditions existing on the valve. Typically, such restrictor valves are actuated due to a back pressure at one axial end, the back pressure moving the blocking element from a release position to a blocking position.

For example, it is from the document EP 1 653 311 A1 is known to automatically regulate a flow rate within a channel section by means of a flap which is actuated via an actuating component, which in turn is biased to a release position and axially actuable by the force of fluid flow to move the flap from the release position towards a blocking position ,

Furthermore, it is from the document DE 10 2007 023 858 A1 known to arrange in a housing of a coolant pump for a cooling circuit of an internal combustion engine, a pressure side arranged, flow rate dependent effective flow control valve, wherein the flow control valve is a ball valve with a cage and arranged therein, gravity and delivery rate dependent acted upon ball.

Due to gravity, the ball is generally in a release position, wherein fluid can flow through a plurality of first openings and through a second central opening. As the fluid pressure increases, the ball is moved to a blocking position in which the ball closes the second opening. In this position, fluid can only flow through the plurality of first openings arranged eccentrically to the second opening. This can be achieved that a vehicle cooling system is not unnecessarily subjected to higher pressures, as may occur in particular when the coolant pump is driven by an internal combustion engine and this is operated in higher speed ranges.

Against this background, it is an object of the invention to provide an improved flow control valve and an improved hydraulic arrangement.

The above object is achieved in the above-mentioned flow control valve according to one aspect of the invention in that the first passage is formed by a valve opening of a valve seat, wherein the second passage is formed by at least one radial recess on the valve opening.

By this measure it is achieved that the first passage can be formed in a structurally simple manner by a valve opening. In other words, the first passage is opened when the locking member is lifted from the valve seat and thus releases the valve opening. On the other hand, the locking position is established when the locking element rests against the valve seat and thus closes the valve opening.

The second passage is formed by at least one radial recess on the valve opening. The second passage can thus be realized in a structurally simple manner, wherein the first passage and the second passage form a common passage when the locking element is in the release position. In the blocking position, fluid may flow past the blocking element through the second passage.

The second passage may be formed by a single radial recess forming a single channel. However, the second passage can also be formed by a plurality of radial recesses arranged distributed over the circumference of the valve opening, which consequently together form the second passage.

According to a preferred embodiment, which constitutes a separate invention in connection with the preamble of claim 1, the second passage is formed by a single passage.

This ensures that in the locked position of the blocking element that of a Fluid supply device provided fluid flows exclusively through the single channel. This can be adjusted in terms of its cross section so that deposits or foreign bodies are then deliberately carried along and can not attach.

The second flow area of the second passage formed by the single passage is smaller than the sum of the first flow area and the second flow area, and thus smaller than a total flow area of the flow restriction valve in the release position. Further, the single passage forming the second passage is preferably formed to have a fixed, non-variable flow area.

The flow-limiting valve is therefore preferably switchable exclusively between two states. The first passage and the second passage are further preferably spatially separated.

By the measure to guide the blocking element in a cage, there is the possibility to flow around the locking element even in the release position, so that even in the release position deposits of foreign bodies can be prevented.

Consequently, jamming or fouling of the flow restriction valve can be reduced or prevented.

By the measure, to store a blocking element on a cage, also contact surfaces can be reduced and the possibility for foreign body or dirt deposits can be reduced.

The blocking element is preferably moved axially between the blocking position and the release position. In the release position, the blocking element is preferably adjacent to the first axial end, which is preferably connected to a pressure side, that is, to a fluid supply device or the like. The second axial end is preferably connected to a hydraulic consumer.

The blocking element is preferably moved in the flow limiting valve according to the invention due to a back pressure in the region of the first axial end of the cage, preferably from the release position to the blocking position.

Consequently, when the back pressure at the first axial end is increased, the first passage is closed by means of the blocking element, so that fluid can only flow via the second passage in the direction of the second axial end.

According to a further preferred embodiment, which constitutes a separate invention in accordance with a second aspect in connection with the preamble of claim 1, a channel forming the second passage is arranged in the gravitational direction at the bottom, so that foreign bodies present in a lower region of the fluid channel axially in the direction can be flushed out to the second end.

In the second aspect of the invention is advantageously achieved that in a lower region of a fluid channel due to gravity existing foreign bodies or deposits can be flushed out in an optimal manner, so that it can be avoided that these foreign bodies affect the function of the flow control valve.

In particular, when only a single channel forms the second passage, a relatively high flow rate can be established in the individual channel, so that rinsing can be promoted.

The channel forming the second passage may be a circular or a polygonal channel as far as the cross-sectional shape is concerned.

Preferably, however, the channel forming the second passage has a circular segment shape in cross section.

The circular segment shape of this channel is therefore limited by a circular arc and a chord.

The channel forming the second passage can thus be partially formed by the cage, which in this case preferably forms the chord of the circular segment shape. The circular arc of the circular segment shape is preferably formed by the fluid channel itself.

The channel forming the second passage is consequently designed in the manner of a "groove" in the lower region of the fluid channel in this case.

If the terms "below" or "above" are used in the present case, these terms generally refer to the direction of gravitation, unless otherwise stated.

The blocking element may be a plate which rests in the blocking position on a poppet valve seat.

Of particular preference, however, it is when the blocking element is a ball.

In this case, a valve seat is formed in particular by an opening in the cage against which the ball comes into abutment in the locked position. The opening is preferably a central opening formed concentric with a longitudinal axis of the cage.

According to a further preferred embodiment, the blocking element is biased by a spring in the release position.

In this way, regardless of the position of the flow-limiting valve (for example, installed in a motor vehicle, which is on a slope or the like) a defined switching due to back pressure occur, as is not possible in a "biased" by gravity valve assembly.

According to another preferred embodiment, the spring extends through an axial opening in the cage, wherein the axial opening forms the first passage.

By this measure, it can be ensured that fluid flowing through the first passage also flows around the spring. This makes it possible to reduce or prevent the adhesion of foreign bodies or the like even in the area of the spring.

The axial opening, which forms the first passage, preferably forms a valve seat for a spherical locking element.

In general, the ratio of the flow cross sections can be configured as desired.

However, it is particularly preferred if the first flow cross section is greater than the second flow cross section.

Furthermore, according to a further embodiment, it is preferred if a damping device, which is designed to damp a movement of the blocking element, is integrated in the flow-limiting valve.

By this measure, it is possible to reduce or avoid unwanted vibrations of the blocking element. This results in an improved NVH behavior and a defined functionality.

In the case of the hydraulic arrangement according to the invention, it is of particular advantage if the fluid supply device has a pump driven by an electric motor, wherein the flow limiting valve is arranged between a pressure connection of the pump and the hydraulic consumer.

It is particularly preferred if a second (further) hydraulic consumer is connected to the pressure connection of the pump.

In this case, by varying the rotational speed of the electric motor and thus changing the fluid pressure provided at the pressure port, switching of the flow limiting valve may be initiated such that either one hydraulic consumer or the other hydraulic consumer receives more hydraulic fluid per unit time (a larger flow rate) Is made available.

This makes it possible to realize the hydraulic arrangement so that two hydraulic consumers are supplied with a pump, which receive more or less hydraulic fluid as needed. The first hydraulic consumer, which is connected via the flow-limiting valve to the pump, is preferably an electric drive machine of a motor vehicle drive train. The further hydraulic consumer is preferably a wet-running multi-plate clutch of the drive train.

Depending on the embodiment, at least one of the following advantages can be achieved with the invention.

By guiding a ball in a cage, it is possible to flow around the blocking element and possibly other elements. By disposing a single channel at the bottom, contaminant particles or deposits can be removed or rinsed out.

In general, the invention makes it possible to realize a volume flow at the lower bottom of the valve for purging of particles, while reducing a slider contact surface.

In general, a volume flow-dependent distribution of hydraulic fluid, in particular cooling oil can be realized.

Due to the flushing volume flow jamming and / or contamination can be reduced or prevented. The advantageous ball design reduces contact areas and also reduces the possibility of dirt deposits.

It is understood that the features mentioned above and those yet to be explained not only in each of the specified Combination, but also in other combinations or alone, without departing from the scope of the present invention.

• 1 eine schematische Längsschnittansicht durch ein Durchflussbegrenzungsventil gemäß einer Ausführungsform der Erfindung;
• 2 eine Schnittansicht entlang der Linie II-II der 1;
• 3 eine Schnittansicht entlang der Linie III-III der 1;
• 4 eine schematische Darstellung einer Ausführungsform einer erfindungsgemäßen Hydraulikanordnung;
• 5 ein Diagramm von Volumenstrom (bspw. in l/min) über einer Drehzahl n eines Antriebsmotors einer Pumpe eines Fluidversorgungseinrichtung;
• 6 eine der 3 vergleichbare Darstellung einer weiteren Ausführungsform eines Durchflussbegrenzungsventils in einer Freigabeposition;
• 7 das Durchflussbegrenzungsventil in einer Sperrposition; und
• 8 eine der 6 vergleichbare Darstellung einer modifizierten Ausführungsform des Durchflussbegrenzungsventils der 6 und 7.

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

• 1 a schematic longitudinal sectional view through a flow-limiting valve according to an embodiment of the invention;
• 2 a sectional view taken along the line II-II of 1 ;
• 3 a sectional view taken along the line III-III of 1 ;
• 4 a schematic representation of an embodiment of a hydraulic arrangement according to the invention;
• 5 a diagram of volume flow (eg in l / min) over a speed n of a drive motor of a pump of a fluid supply device;
• 6 one of the 3 Comparative illustration of another embodiment of a flow-limiting valve in a release position;
• 7 the flow restriction valve in a locked position; and
• 8th one of the 6 Comparative illustration of a modified embodiment of the flow limiting valve of 6 and 7 ,

In the 1 to 3 is shown in schematic form a flow-limiting valve and designated 10.

The flow control valve 10 has a Ka 12 on, which may be made of metal, but preferably made of a plastic. Furthermore, the flow restrictor includes 10 a blocking element 14 , which is advantageously designed here as a ball. The blocking element 14 may be made of metal, but may also be made of plastic.

The Ka 12 is in a housing 16 the flow restriction valve 10 arranged. The housing 16 can be a dedicated housing of the flow control valve 10 be. The housing 16 However, it may also be part of a hydraulic arrangement, for example a hydraulic plate or the like.

In the case 16 is a fluid channel 18 formed, which preferably has a circular cross-section. The Ka 12 is in the fluid channel 18 used.

The flow control valve 10 also includes a spring 20 , by means of the blocking element 14 is biased in a release position FP. Generally, the blocking element 14 at the Ka 12 between this release position FP and an in 1 slidably mounted locking position SP slidably mounted.

The Ka 12 has a first axial end 22 which is preferably connectable to a fluid supply device, and has an opposite second axial end 24 which is preferably connected to a hydraulic consumer.

The Ka 12 has a first passage 26 on. In the release position FP of the blocking element 14 is the first axial end 22 over the first passage 26 with the second axial end 24 fluidly connected. In the blocking position SP, the first passage 26 closed or locked.

The Ka 12 further defines a second passage 28 , which is independent of the position of the blocking element 14 the first axial end 22 with the second axial end 24 combines.

The first passage 26 has a first flow area A ₁ (see 3 ). The second passage 28 has a second flow area A ₂ (see 3 ).

The Ka 12 has a first cylinder portion 30 on, whose outer diameter is smaller than the inner diameter of the fluid channel 18 and whose inner diameter is larger than the outer diameter of the blocking element 14 , The blocking element 14 is within the first cylinder section 30 mounted axially displaceable. Adjacent to the first axial end 22 extends from the first cylinder portion 30 an annular axial stop 32 radially inwardly against which the locking element 14 by means of the spring 20 is pressed in the release position FP.

In the region of the second axial end 24 is the first cylinder section 30 with a radial wall 34 connected, which extends in the radial direction and generally has an outer diameter, the inner diameter of the fluid channel 18 equivalent. The radial wall 34 is in cross section in 3 shown.

It can be seen that in the radial wall 34 a valve seat 33 for the spherical locking element 14 is formed in the locking position SP, the central valve opening 36 which forms the first passage as shown in FIG 1 is indicated.

The Ka 12 also has a second cylinder section 35 up, extending from the radial wall 34 extends in the opposite axial direction. The second cylinder section 35 flows into the opening 36 in the radial wall 34 ,

The feather 20 is as a coil spring 38 educated. The coil spring 38 has an outer diameter that is smaller than an inner diameter of the second cylinder portion 35 and smaller than a diameter of the opening 36 , The coil spring 38 extends into the second cylinder section 35 in and is supported axially on the Ka 12 from, preferably on a radial end wall 39 whose diameter is the inner diameter of the fluid channel 18 equivalent.

As it is in 1 can be seen, the coil spring extends 38 in the release position FP in the axial direction from the second cylinder section 35 and out of the opening 36 out and into the first cylinder section 30 into where the coil spring 38 on the blocking element 14 is applied. In the locking position SP, the coil spring 38 completely in the second cylinder section 35 compressed into it.

An outer diameter of the second cylinder section 35 is preferably smaller than an outer diameter of the first cylinder portion 30 ,

A damping device 40 may, for example, be formed by a plate-shaped element extending in the radial direction, which with the blocking element 14 is rigidly connected and that in a central region of the spring, in particular coaxially within a helical spring 38 is arranged.

In the first cylinder section 30 is a plurality of fluid ports 42 educated. From the side of the first axial end 22 inflowing fluid may initially in the release position FP in a space between the outer periphery of the first cylinder portion 30 and the inner periphery of the fluid channel 18 flow and then through the fluid ports 42 in the interior of the first cylinder section 30 in, and thereby preferably on the blocking element 14 over in the direction of the opening 36 and in the second cylinder section 35 into it.

The second cylinder section 35 also has a plurality of radial passage openings 44 through, through the opening 36 inflowing fluid radially into an outer region between the outer periphery of the second cylinder portion 35 and the inner periphery of the fluid channel 18 can flow. From this area, the fluid can either continue in the axial direction through an opening in the end wall 39 through, or else, as in 1 is shown, in the radial direction to the outside via a fluid port 46 in the case 16 ,

The flow direction of the fluid is in 1 through arrows 50 indicated. In 1 It can also be seen that regardless of the axial position of the blocking element 14 always a certain amount of fluid through the second passage 28 in the direction of the outer circumferential space around the second cylinder portion 35 can flow around.

The second passage 28 is arranged at the bottom in the direction of gravity and forms a channel through which foreign bodies can be flushed so that they can not impair the function of the blocking element. Also the fact that the blocking element and the valve seat passing through the opening 36 is formed, are flushed in the release position FP, helps to ensure that foreign matter, the function of the flow control valve 10 can not affect.

The first flow cross-section A ₁ is preferably larger than the second flow cross-section A ₂ (see 3 ).

In 2 it can be seen by way of example that in the first cylinder section 30 two diametrically opposite fluid openings 42 may be formed, each extending over a peripheral region of less than 90 °. It is understood that in the cylinder section 30 as well as in the cylinder section 35 , in each case also fewer or more openings 42 may be present, which are preferably arranged distributed uniformly over the circumference. In some cases, the cylinder sections may be formed by a plurality of circumferentially formed webs, between each of which the fluid openings 42 extend.

In 4 is an embodiment of a hydraulic system 60 shown. The hydraulic system 60 has a fluid supply device 62 on. The fluid supply device 62 includes a pump 64 that by means of an electric motor 66 is driven, with a variable speed n, as in 4 is indicated.

The pump 64 has a suction connection with a tank 68 or another low-pressure area is connected. Furthermore, the pump points 64 a pressure port on which a volume flow Q _{G is} provided.

The hydraulic system 60 further includes a first hydraulic consumer 70 , For example, a cooling device for an electric drive motor of a motor vehicle, and a second hydraulic consumer 72 , For example, a disk set of a wet-running multi-plate clutch of a such motor vehicle powertrain. The pressure connection of the pump 64 is via a flow relief valve 10 with the first hydraulic consumer 70 connected, such that the first axial end 22 facing the pressure port and the second axial end 24 the first hydraulic consumer 70 is facing. The flow control valve 10 In terms of design and operation preferably corresponds to the flow control valve 10 of the 1 to 3 ,

The pressure connection of the pump 64 is also directly with the second hydraulic consumer 72 connected.

The hydraulic connections and the flow control valve 10 between the pressure port of the pump 64 and the hydraulic consumers 70 . 72 form a distribution facility 74 ,

The first hydraulic consumer 70 and the flow restriction valve 10 forms a hydraulic resistance R ₁ . The second hydraulic consumer 72 forms a second hydraulic resistance R ₂ .

The distribution facility 74 is designed to be the first consumer 70 a volume flow Q ₁ is provided, and the second hydraulic consumer 72 a volume flow Q ₂ . It is Q _G = Q ₁ + Q ₂ .

At low speeds n, the flow limiting valve is located 10 in the release position. This is the first hydraulic consumer 70 preferably provided a relatively high volume flow Q ₁ , and the second hydraulic consumer 72 a relatively low volume flow Q ₂ .

Upon reaching a threshold speed n _s (see 5 ) turns this ratio around, so that at speeds greater than or equal to n _s the second hydraulic consumer 72 a larger volume flow Q ₂ is provided as the first hydraulic consumer 70 , which receives a volume flow Q ₁ . This reversal of the volumetric flow ratios is achieved by switching over the flow-limiting valve 10 , Which at the speed n _s such a back pressure in the region of the first axial end 22 learns, so that the blocking element 14 against the force of the coil spring 38 is pressed into the blocking position SP, so that subsequently fluid only through the second passage 28 towards the first hydraulic consumer 70 can flow.

In the 6 and 7 is another embodiment of a flow control valve 10 ' shown. The flow control valve 10 ' includes a cage 12 ' , where in the 6 and 7 only a radial wall 34 ' thereof is shown. At the radial wall 34 ' is a valve seat 33 formed having a circular opening 36 provides. As with the above embodiments, the aperture provides 36 the first passage 26 represents.

Furthermore, in the 6 and 7 shown at the valve opening 36 a radial recess 28 ' is formed, which is approximately crescent-shaped in plan view. In the in 6 shown release position forms the radial recess 28 ' together with the first passage 26 a total passage. In contrast to the above embodiments, the first passage 26 and the second passage 28 ' consequently connected together in the release position FP.

7 shows the blocking position at which the blocking element 14 in the form of a ball, the valve opening 36 closes by the blocking element 14 at the valve seat 33 is applied. In the blocking position SP, the second passage thus remains for fluid 28 ' which is formed by the radial recess, as in 7 is indicated.

8th shows a modified embodiment of a flow-limiting valve 10 " , in terms of design and operation generally the flow control valve 10 ' of the 6 and 7 equivalent. While at the flow control valve 10 ' of the 6 and 7 the second passage 28 ' is formed by a single radial recess, are in the flow control valve 10 " of the 8th three distributed over the circumference arranged radial recesses 28a " . 28b " . 28c '' provided, which together form the second passage.

In the in 8th shown release position FP is the total passage thus formed by the valve opening 36 and the three in plan view crescent-shaped radial recesses 28a " . 28b " . 28c " , In the in 8th not shown, only the second passage is opened, which is formed in this case by the three radial recesses 28a " . 28b " . 28c " whereas in the locked position the valve opening 36 is closed, as in the presentation of 7 ,

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

• EP 1653311 A1 [0004]
• DE 102007023858 A1 [0005]

Claims (11)

A flow restriction valve (10) having a cage (12) insertable into a fluid channel (18) and having a first axial end (22) and a second axial end (24), and a locking member (14) attached to the first Cage (12) between a locking position (SP) and a release position (FP) is movable, wherein the cage (12) is formed so that in the release position (FP) of the locking element (14) the first and the second axial end (22 , 24) are interconnected via a first passage (26) and a second passage (28), the first passage (26) defining a first flow area (A ₁ ), the second passage (28) having a second flow area (A ₂ ), and wherein the cage (12) is further configured such that in the blocking position (SP) of the blocking element (14) the first axial end (22) and the second axial end (24) only via the second passage (28 ), characterized in that he The passage (26) is formed by a valve opening (36) of a valve seat, wherein the second passage (28) is formed by at least one radial recess on the valve opening (36). Flow restrictor nA 1 or according to the preamble of Claim 1 , characterized in that the second passage (28) is formed by a single passage. Flow limitation valve after Claim 1 or 2 or after the generic term of Claim 1 characterized in that a channel forming the second passage (28) is disposed below in the gravitational direction (G) so that foreign matter present in a lower portion of the fluid passage (18) can be flushed out axially toward the second end (24) , Flow limitation valve after Claim 1 - 3 , characterized in that at least one channel forming the second passage (28) is circular-segment-shaped or sickle-shaped in cross-section. Flow control valve according to one of Claims 1 - 4 , characterized in that the blocking element (14) is a ball. Flow control valve according to one of Claims 1 - 5 , characterized in that the blocking element (14) by means of a spring (20) is biased in the release position (FP). Flow limitation valve after Claim 6 characterized in that the spring (20) extends through an axial opening (36) in the cage (12) forming the first passage (26). Flow control valve according to one of Claims 1 - 7 , characterized in that the first flow cross section (A ₁ ) is greater than the second flow cross section (A ₂ ). Flow control valve according to one of Claims 1 - 8th characterized by damping means (40) adapted to damp movement of the blocking element (14). Hydraulic arrangement (60) with a fluid supply device (62), with a hydraulic consumer and with a flow-limiting valve according to one of Claims 1 - 9 , Hydraulic arrangement after Claim 10 , characterized in that the fluid supply device (62) has a by means of an electric motor (66) driven pump (64), wherein the flow limiting valve (10) between a pressure port of the pump (64) and the hydraulic consumer (70) is arranged.

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