DK164298B - Non-return valve - Google Patents

Description

in

DK 164298 B

The invention relates to a non-return valve of the kind mentioned in the preamble of claim 1. Check valves are inserted in several ways to prevent reflux flow as well as valves which prevent the discharge of a conduit in the flow direction 5 after disconnection of the pre-pressure. The shut-off force applied in the shut-off direction on the shut-off body can be produced by a closing spring or by the self-weight of the shut-off body by corresponding vertical mounting of the check valve. Crucial to the shut-off quality is the relationship between valve body and valve seat, which is particularly advantageous when the movable valve body includes a spherical closure surface which is relatively hard and which cooperates with a softer material of conical or angular valve seat. The valve seat can then be finely adapted to the ball surface of the movable valve body so that a rotation of the valve body does not cause any sealing disadvantages.

In such a non-return valve, it is necessary to have provided an opportunity for flow outside the radial guide, ie a connection between the areas upstream and downstream of the radial guide, which flow outside the radial guide must be provided throughout the opening height of the movable valve body. and furthermore, a considerable amount of space is required, especially with regard to the diameter of the check valve.

In U.S. U.S. Patent No. 3,457,949 discloses a counter valve of the type mentioned in the preamble, wherein the spherical closure surface of the movable valve body abuts against a bowl-shaped workpiece with a larger diameter than the valve body, and in the cup-shaped body radial grinding is provided, while a closing spring supports on the bottom of the workpiece.

The larger diameter of the bowl-shaped body, which is more than twice the radius of the spherical closure surface, results in a correspondingly larger overall diameter in the check valve.

It is an object of the invention to provide a non-return valve of the kind referred to initially if

DK 164298 B

the overall diameter is as small as possible and where the frictional force generated by the valve body guide is as small as possible.

The object is achieved with a check valve according to the characterizing part of claim 1.

In contrast, the characteristic valve of the invention according to the invention of claim 1 has the advantage that the movable valve body is guided radially with low friction, and since the advantages of a ball valve 10 are maintained, the flow of media can flow through the cutout at a minimal external dimension of the valve. Because of the radial guide, a self-centering of the valve body with respect to the ball face facing the valve seat is provided by the media flow, so that good seal in the check valve is ensured due to the continuous mating of valve seat and valve body. It is further advantageous that a non-return valve provided by the invention can be incorporated with minimal space requirements in houses which also serve for other purposes, for example by drilling an existing duct for the flow-through bore. Said mating can also be affected by various material combinations, for example, by a housing with a plastic valve seat and a movable valve body of metal, especially steel, and vice versa with a metal housing and a ball of plastic.

According to an advantageous embodiment of the invention, the cuts provided in the valve body are symmetrically centered so that the valve body provides a self-centering at the media flow so that a further axial guide of the valve body, in addition to the radial guide, 30 is not necessary.

According to a further advantageous embodiment of the invention, the valve body can be loaded with a closing spring which affects a surface located on the valve body transversely of the opening direction. This surface may be produced in various ways, advantageous being that it is as close as possible to the actual sealing surface of the check valve.

DK 164298 B

3, thereby allowing the longest possible closing spring and thus a correspondingly long movement of the movable valve body. The closure spring may be configured as a thread spring (screw spring), but may also be provided as an elastic block or a leaf spring. Some of the windings may be block-shaped for guiding reasons.

According to a further advantageous embodiment of the invention, in the spherical surface on the face of the valve seat facing the valve body across the flow direction and in the area between valve seat and guide, an annular groove is provided from which the cut-outs for media flow are provided. Such an annular groove not only reduces the weight of the movable valve body without, therefore, adversely affecting the radial guide, but at the same time acts as a conduit for the medium.

According to a further advantageous embodiment of the invention, a valve bore is provided in the valve body on the side facing away from the valve seat, which also contributes to the weight reduction of the valve body and whose bottom surface can act as a stop for the closing spring. In addition, in this tap bore, channels which act as cut-outs can open. In that the closing spring is at least partially absorbed by this pin bore, the overall spring length can also be increased by the advantage mentioned above, by being able to provide a valve with a relatively small length dimension. In addition, according to the invention, the spring can also be designed such that the part of the spring placed in the pin bore can be designed as a spring block, thereby providing an additional axial guide. According to the invention, the back of the ball may be further flattened, in extreme cases down to the bottom surface of the pin bore.

According to the invention, for the media flow, i.e. for the flow passage, said cuts in the area from the bore upstream of the radial guide to the downstream area 35 provided for the guide have been designed differently.

Only. a radial guide must be maintained at all times 4

DK 164298 B

movable valve body. Thus, according to the invention, cut-outs can act as connecting channels connecting the two regions, passing from the above-mentioned pin bore to the above-mentioned annular groove on the valve body, 5 without the spherical shape in the sealing region, respectively. the driving area is adversely affected. However, the cut-outs can also be provided in the casing surface of the ball, since in boundary cases, that is, in case of substantially large cuts, only pieces of connection to the radial guide and a ball ball 10 to the sealing point remain.

According to a further embodiment of the invention, the non-return valve may be designed as a double non-return valve with a first valve body acting in only one flow direction and with a second valve body acting in the opposite flow direction 15. In this way, a wiring at low pressures can also be provided, e.g. to prevent an outlet from a conduit, but on the other hand, throughput is ensured in both directions.

Advantageously, the second movable valve body 20 may be provided in a centered bore of the first movable valve body, which similarly acts as a flow passage for the second flow direction. Hereby, the predetermined minimum dimension of a spherical valve body is utilized at the location 25 of an additional check valve without increasing the diameter. In connection therewith, the centered bore may be configured as a stepped bore whose tapered edges act as a valve seat. In this embodiment, since the media flow can only proceed in one or the other direction, according to the invention, the coil spring in the second movable valve body can, without alteration of the actual opening force, support a chest on the valve housing attached to the first movable valve body, since the second valve body only opens when the first valve body is closed. This, above all, provides a structural simplification.

DK 164298 B

5

According to a further advantageous embodiment of the invention, the non-return valve provided by the invention can be used in a combustion engine propellant injection system, and in particular as a pressure relief valve. At 5 fuel injection plants, high frequencies and thus very short connection times for simultaneous high pressures occur, the check valve having to close further, since the leakage currents can cause a significant disturbance in the uniform distribution. When used as a pressure relief valve, the cut-outs can be designed so that, in connection with the shut-off process, they provide one throttle action which can be used in connection with the so-called fuel fitting.

Of course, the non-return valve provided by the invention can also act as a pressure retention valve, that is, in cases where the pressurized surfaces and spring force constitute the decisive control values. Due to the fact that the invention provides a fundamentally sealing surface on the movable valve body 20 as a sealing surface, and that the guide through the spherical configuration in this area of the valve body is only linear, characteristics which are well-controlled are provided for the construction. Of course, in addition to a ball, a valve body provided by the invention can also be provided from another formed blank, although the sealing surface must be fundamentally shaped as a ball bead and the radial guide must also be formed in the arch.

According to a further advantageous embodiment of the invention, the movable valve body cooperates with a device which dampens the opening and / or closing movements of the body. Such a damping device may be desirable in connection with many applications, since the check valve provided by the invention is initially a rapidly opening and closing valve with a minimum frictional force, with large guide surfaces and possibly with relatively low spring force. In connection with the invention 6

DK 164298 B

the chamber may act as a damping device, the volume of which is changed by the movement of the movable valve body, and which is also provided with a throttle opening, and the space being provided as a cylindrical tap bore extending in the direction of movement of the valve body, the cylindrical bore or damping piston being connected to the movable valve alloy. Thus, for example, a pin provided on the movable valve body can act as a damping piston.

10. According to an advantageous embodiment of this damping device, the parts contained therein, such as, for example, a nipple provided with the tap bore, or the damping valve, can act as a limiting stop for the opening height of the movable valve body. Such an abutment may, of course, also be provided through the bottom of the pin bore or be formed in the face of the pin respectively. damping piston.

According to a further embodiment of the invention, the cut-outs are formed as sloping seals so that the passage cross-section between the valve body and the housing can be largely kept constant. In addition to this machining of the valve body, the carvings of the invention can also be provided by electro-erosive machining, for example, in a provided, already cured ball, electro-erosively placed, the desired cut-outs in such a way that only the ball carcass on the sealing side and parts of the radial guide remains in the bore. In this way, it is especially operationally possible to make the valve body provided by the invention from balls produced in 30 large series with an excellent surface.

Further advantages and advantageous embodiments of the invention will become apparent from the following description, claims and drawings.

Several exemplary embodiments of the invention 35 are explained in more detail below with reference to the drawing, in which:

DK 164298 B

7 FIG. 1 and 2 are a view of the first exemplary embodiment in longitudinal and transverse sections; 3 and 4 are a view of the second and third exemplary longitudinal embodiments; 5 and 6 are a view of the fourth exemplary embodiment in longitudinal and transverse sections; 7 is a cross-sectional view of the fifth exemplary embodiment; Figure 8 is a view of the sixth exemplary embodiment as two check valves with a spring; 9 is a view of the seventh exemplary embodiment formed as a double check valve; FIG. 10 is a view of the embodiment of FIG. 1 shows the first exemplary embodiment as a variation with a damping device; FIG. 11 is a view of the eighth exemplary embodiment with a further variation of a damping device.

In the embodiment shown in FIG. 1 and 2, a first exemplary embodiment is provided in a centered bore 1 in a valve housing 2, a movable valve body 3 which is radially and axially moved. To the valve housing 2 is provided an insert ring 4, on which the valve body 3 rests, which is provided with a valve seat 5. The valve body 3 is pressed 25 by a closing spring 6 against the valve seat 5.

On the side facing the valve seat 5, the movable valve body 3 is formed as a ball face 7 which, in connection with the flow direction, is provided with radial cuts formed as discharges 8 for the media flow. As soon as the valve body 3 is lifted from the seat 5, the medium inside the bore 1 can flow out from the area 9, over the discharges 8 and into the area 10, whereby the portion of the ball surface remaining between the bores 8 acts as guide 11 in the bore 1. On the away from the valve seat 5 facing side of the valve body 3 is provided a pin 12 and a surface 13 extending transversely of the flow direction.

DK 164298 B

8 which the closing spring 6 supports. The closure spring is here designed as a threaded screw spring, but may equally well be formed as an elastic cylinder or cone-shaped spring or otherwise.

5 Although the ring 4 is formed with a cone surface 14 on the side facing the valve body 3, the actual seal lies along a line 15. This line 15 is in each case within the region of the ball surface 7 where no cuts are provided, thus that a cutting 10 with the discharges 8 cannot occur.

Especially in this first exemplary embodiment, the movable valve body 3 is made from a ball, with corresponding machining, that is to say, by placing the cut-outs, the pin 12, the surface 13 and the 15 discharges are provided. As a ball, a large series is preferably provided. metal ball, the machining of which is, for example, provided by an electro-erosive process in which the remaining part of the ball surface is not adversely affected in terms of quality, ie. hardness and 20 smoothness. After all, this quality of the ball surface 7 is a measure of the seal quality in the valve seat 5 and the quality of the guide 11.

In FIG. 3 is shown the second exemplary embodiment of the invention, the valve housing and valve seat being rendered very simplified to clarify the details of the longitudinal section shown valve body 3. Also in this exemplary embodiment, the movable valve body is formed by a ball and according to the invention is guided radially. In addition, the movable valve body is formed with a tap bore 16, 30 on whose bottom surface 17 the closing spring 6 supports, in relation to the flow direction, inclined extending connecting channels 18 in the valve body connecting the area 9 to the tap bore 16 are provided as soon as the movable valve body 3 is lifted. from the seat, after flowing medium 35, it may extend beyond the area 9, over the connecting channels 18 in the pin bore 16 and from there further un-controlled by the check valve.

DK 164298 B

9 In the embodiment of FIG. 4 shows the exemplary embodiment of the invention, the ball surface is formed with an annular groove 19 downstream of the valve seat 5, which on the one hand results in a reduction in the weight of the movable 5 valve alloy, and on the other provides an improvement in the flow connections with the cuts. . The volume of the area 9 is thereby increased. As cuts, as in the first exemplary embodiment, discharges may act, or also, as in the second exemplary embodiment, ducts or also some channel around the passage of the shutter body extending into the shutter body. In each case, the annular groove 19 is so far from the sealing line 15 that a cut with the valve seat 5 is prevented. In addition, in connection with this exemplary embodiment, it is further noted that it is flattened away from the valve seat 5 on the movable valve body, thereby providing a plane 20 which the closing spring 6 supports.

In the embodiment shown in FIG. 5 in longitudinal section and in FIG. 6 shows a fourth exemplary embodiment of the invention, the movable valve body 3 is formed as a ball, on the back of which are provided two deep, intersecting intersections 22 which extend beyond the guide 11 in the direction of the valve seat 5. This is achieved. on the one hand, a substantial reduction in weight, without therefore reducing the radial guide 11. The closing spring is not shown here, but may, as in the other exemplary embodiments, be designed in different ways. In any case, they can be supported on the cut-bottom 23 in the deep cut-outs 22. However, they can also be supported on the four remaining columns 24. The deeper the cut-outs 22 are carried, the greater the flow cross-section from the area 9 over the cut-outs 22 is provided.

In the embodiment shown in FIG. 7 illustrates the fifth exemplary embodiment 35 of the invention, the movable valve body is also configured as a ball shown in cross section. foundations

DK 164298 B

10, this exemplary embodiment corresponds to the first exemplary embodiment, however, the discharges explained in the first exemplary embodiment are here extended to deep cuts 25. Hereby, only 5 pieces are left in the radial guide according to the invention, these deep cuts 25 is assembled with a configuration as in the first exemplary embodiment with a pin or as in the second exemplary embodiment with a pin bore.

10 In FIG. 8, as the sixth exemplary embodiment of the invention, an application is shown in an injection system, in which the non-reproducing valve body 3 which can have any embodiment of the invention is located in a bore 27 in the housing which is closed with a tapered nipple 28, the opening edges of which act as a valve seat for another valve body 29, the back of which of which the closing spring 6 supports. Thus, in a fuel injection system, the fuel can flow from both sides over the valve bodies 3 and 29, and then be able to flow away through an outlet 30 in the space in which the spring 6 is located. Of course, the use of this exemplary embodiment is not limited to injection plants, but there are very advantageous applications for this in such very complicated plants. The valve body 3 is shown here in the opened state.

The FIG. The seventh exemplary embodiment of the invention is also particularly advantageous for use in an injection system, the seventh exemplary embodiment of the invention being designed as a double convoy. While the fundamental structure of the movable valve body may be provided as in the other exemplary embodiments, in this case, the movable valve body 3 as the first valve body is provided coaxially with a second valve body 31 which opens in the opposite direction of the first valve body and which controls a second flow opening 32 within the first valve body,

DK 164298 B

11 and which is also affected by a closing spring 33. While the first movable valve body 3, as in the second exemplary embodiment, is guided radially in a bore in the valve housing 2 and is influenced by a closing spring 6, the second 5 movable valve body 31 is guided in a region. of larger diameter in a stepwise bore 34 radially, which bore is located in the center of the movable valve body 3, and wherein the annular breast 35 acts as a valve seat. Although this second movable valve body 31 may actually be constructed 10 in the same manner as in the other exemplary embodiments, it is here in FIG. 9, corresponding to the first exemplary embodiment. The closing spring 33 for this second valve body 31 rests on a chest 36 of the valve housing 2. Depending on the direction of flow of the medium to be controlled, 15 opens either the first or second check valve.

When used in fuel injection systems, this seventh exemplary embodiment of the invention may be configured as a direct pressure relief valve, the housing 2 being designed as a screw nipple which is capable of being screwed into an injection pump housing 37 at the end of a pressure passage 38. the end of this nipple can be screwed onto a thread 39 by a pressure line leading to the injection nozzle. During the high-pressure injection process, the fuel flows through the second check valve 31, 32 and 35 and the flattened piece 40 of the second movable valve body 31 to the injection nozzle. After completion of the injection, the first movable valve body 3, due to the dynamic pressure provided in the pressure line, is lifted so long from the associated valve seat 5 that the overpressure is degraded to normal filling pressure. Due to the relatively large cross-section, this pressure degradation is provided very quickly with a minimum of harmful space. Of course, if some form of adjustment or additional pressure relief is desired, the first movable valve body 3 may be provided with additional throttle means.

DK 164298 B

12, which may, for example, have different throttle effect depending on the opening height. In addition, the characteristics known in connection with injection by so-called pressure valves can be transferred to the invention, with corresponding changes in the original invention, namely the ball seat and the spherical guide of the check valve.

In FIG. 10 is shown a variant of the first exemplary embodiment with a damping device. The pin 12 of the movable valve body 3 here dives into a cylindrical pin bore 41 in a nipple 42 formed with a flange 43. This flange 43 is inserted into the center bore 1 of the housing 2 and is secured against displacement by a fuse ring 50. In addition, the closing spring 6 with the end of the movable valve body 3 supports this flange 43. Throughflow of the medium, flow openings 44 are provided in the flange 43.

The pin 12 is radially strongly sealed in the cylindrical pin bore 41, and a throttle bore 45 having a predetermined cross-section is provided at the bottom of this cylindrical pin bore, so that the pin 12 at the axial movement of the valve body 3 in the cylindrical bore 41 acts as a piston which either presses outwardly on the medium through opening through the throttle bore 45 or sucks inwardly upon closing. When the closing spring 6 is provided 25 with sufficient force, the check valve can also be closed while providing a negative pressure in the pin bore 41, which gradually builds up over the throttle bore 45 after the closing process. Conversely, the closure spring 6 can of course also be designed so weak that the closure process is delayed due to the negative pressure. Instead of a throttle bore 45, a radial clearance between the pin 12 and the inner wall of the cylindrical pin bore 31 may provide the throttle action, or throttle channels may be provided by the invention in this inner wall and / or the pin. predetermined choke section.

In FIG. 11 is a variant of the third of FIG. 4

DK 164298 B

13, although together with a further exemplary embodiment. A base plate 46 secured to the housing is provided with a pin 47 which projects into a corresponding axial pin bore 48 on the movable valve body 49. Here, either a separate choke bore may be provided in the pin bore 48, or the casing surface may also be provided. notes on the pin 47 or in the wall of the pin bore 48 are provided which act as predetermined throttle passages, or the throttle action may be provided at the slot itself. The baseplate 46 acts here as a seal for the closure spring 6 and is formed with flow openings 51 for the media flow.

These devices additionally act as abutments, thereby limiting the maximum opening height of the movable valve body 3 and 49, respectively. In the variant shown in Fig. 10, the abutment is provided in that the face 52 of the nipple 42 after returning the movable valve member 3 opening motion abuts a bottom 55. In the variant shown in Figure 11, the opening height is limited by the front 53 of the pin 20 47 abutting the bottom 54 of the pin bore 48.

In FIG. 11 is shown the eighth exemplary embodiment of the invention. In order to provide a substantially constant flow cross-section after opening the check valve, on the movable valve body 49 provided by the invention, three cut-offs 56 are formed, the surfaces of which approach the pin 47 in the flow direction.

The further down these joints begin, the greater the radial flow cross-section, because of the spherical shape, so that the upwardly increasing distance 30 between the sanding surfaces and the wall of the bore results in a total adaptation to this flow cross-section.

Claims (12)

A non-return valve with a movable valve body (3), which valve body is formed with a spherical surface (7) which cooperates sealingly with a valve seat (5) and which is located in a housing and which includes a flow opening, wherein the valve body is radially guided in a bore which extends in the opening direction and acts as a flow opening and in which the valve body has recesses for the media flow upstream of the valve seat, which recesses connect the areas downstream and upstream of the radial guide and each other the valve body is actuated by a force acting in the closing direction, "k characterized in that the valve body (3) is preferably made of a ball, that the spherical surface (7) is held in the region of the radial guide (11) so that a linear radial contact of the bore (1) is provided and so that the cut-offs (8,18) for the media flow originate from the spherical surface (7) between the valve seat region (5) and the radial guide (11), (see in particular 20 fig. 1 and 3). Check valve according to claim 1, characterized in that the cut-outs (8,22,25), for maintaining the control and guiding position (centering) of the valve body (3), are located centrally symmetrically in the valve body (3) (Figs. 1, 25 6 , 7). A non-return valve according to claim 1 or 2, characterized in that the force acting in the closing direction is provided by a closing spring (6.33) which acts on a surface (13,17,20) located on the transverse direction of the opening. the body (3,31,49) (Figs. 1, 3, 9, 11). Check valve according to claims 1-3, characterized in that part of the cut-outs is formed by a transverse flow direction in the spherical surface (7) and in the area (9) between the valve seat (5) and the guide (11) annular groove (19) (Fig. 4). 5. Check valve according to claims 1-4, characterized in that a tap bore (16, 48) is provided in the valve body (3, 49) on the side facing away from the valve seat (5). 3 and 11). 6. Check valve according to claims 1-5, characterized in that the cut-outs (8, 21, 25, 56) are located on the valve body (3, 49) which is open in the direction towards the wall of the bore (1) ( Figures 1, 4, 7, 11). Check valve according to claims 1-5, characterized in that at least part of the cut-outs (18) 10 are passed through the valve body (3) (Fig. 3). Check valve according to claims 1-4, characterized in that the valve body (3) is provided on the side facing away from the valve seat (5) with notches (22), whose notch bottom (23) is connected to the area (9) upstream of guide (11) (Figures 5 and 6). Check valve according to claims 1-8, characterized in that the valve is designed as a double check valve with a first movable valve body (3) operating in a flow direction and with a second movable valve body 20 (29, 31) acting in a different flow direction (Figs. 8 and 9). Check valve according to claim 9, characterized in that the second movable valve body (31) opens in the opposite direction of the first movable valve body (3) 25 and is located in a centered bore (34) in the first movable valve body (3), which acts as a corresponding flow opening (32). Check valve according to claims 1-10, characterized in that the movable valve body (3, 49) cooperates with a damping device (12, 41, 47, 48) for the opening and / or closing movement of the movable valve body (FIG. 10 and 11). Check valve according to claims 1 to 11, characterized in that the movable valve body is made of a non-metallic material, in particular a ceramic material.