阅读说明：本技术 预控制的液压的方向-***式阀 (Pre-controlled hydraulic directional plug-in valve ) 是由 W.雷思 B.乌尔劳布 B.阮-宣 J.沃尔夫 于 2019-06-19 设计创作，主要内容包括：本发明涉及一种预控制的液压的方向-插入式阀,带有有待插入到液压块的插入式钻孔中的插入式插座,所述插入式插座具有内钻孔并且朝着其前方的端侧具有带有外部的第一密封直径的第一插座区段并且朝着其后方的端侧具有带有外部的第二密封直径的第三插座区段以及具有在第一插座区段和第三插座区段之间的第二插座区段。(The invention relates to a pre-controlled hydraulic directional plug-in valve having a plug-in socket to be inserted into a plug-in bore of a hydraulic block, the plug-in socket having an inner bore and having toward its front end a first socket section with an outer first sealing diameter and having toward its rear end a third socket section with an outer second sealing diameter and having a second socket section between the first socket section and the third socket section.)

1. A pre-controlled hydraulic directional plug-in valve having a plug-in socket (15) to be inserted into a plug-in bore (31) of a hydraulic block (30), which plug-in socket has an inner bore (16) and, toward its front end face (29), has a first socket section (34) with an outer first sealing diameter (D1) and, toward its rear end face, has a third socket section (42) with an outer second sealing diameter, which is larger than the sealing diameter in the first socket section (34), and has, between the first socket section and the third socket section, a second socket section (37) in which the plug-in socket has a row of radial openings (45) and in which the plug-in socket has, in a region and in each case over a certain distance, an outer diameter (D2) on both sides of the radial openings (45), the outer diameter is greater than a first sealing diameter (D1) of the outer portion and less than a second sealing diameter (D3) of the outer portion; and a control slide valve (18) which has a slide valve flange (60) for the hydraulic actuation thereof and is guided in the axial direction in an inner bore (16) of the plug-in socket (15), and the flow cross section between the inner bore (16) and the radial opening (45) of the plug-in socket (15) can be controlled by means of the control slide valve, wherein the control slide (18) is guided at least behind the radial opening (45) on a guide diameter (D4) of the plug-in socket (15) and the inner diameter of the plug-in socket (15) is at least as large as the guide diameter (D4) up to the radial opening (45), characterized in that the ratio between the first outer sealing diameter (D1) and the guide diameter (D4) for the control slide (18) is in the range between 1.10 and 1.28.

2. The pre-controlled hydraulic directional valve as set forth in claim 1, wherein a ratio between the outer first sealing diameter (D1) and the pilot diameter (D4) is in a range between 1.12 and 1.27, in particular in a range between 1.12 and 1.25.

3. Pre-controlled hydraulic directional valve according to claim 1, wherein a control slide (18) with a valve seat control edge (56) interacts with an inner step (47) on the plug-in socket (15) between the radial opening and the front end face (29) in the inner bore (16) upstream of the radial opening (45) of the plug-in socket (15), wherein the control slide (18) is guided axially at least behind the radial opening (45) on a guide diameter (D4) of the plug-in socket (15), and the inner diameter of the plug-in socket (15) up to the radial opening (45) is at least as large as the guide diameter (D4), and wherein, the ratio between the outer first sealing diameter (D1) and the guide diameter (D4) is in the range between 1.10 and 1.22.

4. The pre-controlled hydraulic directional valve according to claim 3, wherein the ratio between the outer first sealing diameter (D1) and the pilot diameter (D4) is in the range between 1.12 and 1.20.

5. The pre-controlled hydraulic directional valve as claimed in claim 3 or 4, wherein the inner diameter (D5) of the plug-in socket (15) is substantially constant from the front end face (29) up to the inner step (47), and wherein the ratio between the outer first sealing diameter (D1) and the inner diameter (D5) of the plug-in socket (15) lies in a range between 1.10 and 1.30, in particular between 1.15 and 1.25, from the front end face (29) up to the inner step (47).

6. The pre-controlled hydraulic directional valve as set forth in the preceding claim, wherein the second socket section (37) has a constant outer diameter (D2), and wherein the ratio between the constant outer diameter (D2) and the pilot diameter (D4) of the second socket section (37) lies in a range between 1.15 and 1.35, in particular in a range between 1.20 and 1.30.

7. The pre-controlled hydraulic directional valve according to the preceding claim, wherein the inner step (47) has a width on the plug-in socket (15) in the range between 0.8mm and 1.7mm, in particular in the range between 1mm and 1.5 mm, in particular 1mm or 1.5 mm.

8. The pre-controlled hydraulic directional valve as set forth in the preceding claim, wherein a circumferential rounded relief notch (44) is present on the outside at the transition from the first socket section (34) to the second socket section (37), in which relief notch the outer diameter of the plug-in socket (15) is smaller than the outer first sealing diameter (D1).

9. The pre-controlled hydraulic directional valve according to the preceding claim, wherein the plug-in socket (15) has a circumferential groove (46) on the inside in the region of the radial opening (45), and wherein the depth of the circumferential groove (46) is preferably approximately 2 mm.

10. The pilot-controlled hydraulic directional valve according to the preceding claim, wherein the pilot spool (18) has an axial bore (70) which is located in the flow path between the two end faces (55, 71) of the pilot spool (18), wherein the axial bore (70) has a first diameter (D7) from the front end face (55) of the pilot spool (18) which is located in the region of the inner step (47) of the plug-in socket (15) via a certain path section and then has a second, smaller diameter (D8), and wherein the transition between the two diameters on the pilot spool (18) is such that, as seen from the front end face (55), the transition is also located behind the radial opening (45) depending on the size of the stroke of the pilot spool (18).

11. The pre-controlled hydraulic directional valve as set forth in claim 10, wherein a bevel (74), preferably a 30 ° bevel, is located on the edge between the axial bore (70) and the front end face (55) of the control slide (18).

12. The pilot-controlled hydraulic directional valve as claimed in the preceding claim, wherein the pilot spool (18) has an annular groove (58) running around on the outside thereof for receiving a sealing ring (59), and wherein the position of the annular groove (58) on the pilot spool (18) is such that, when the pilot spool (18) is seated on the inner step (47) of the plug-in socket (15), the annular groove (58) is located in the region of the second socket portion (37) as viewed in the axial direction.

13. The pre-controlled hydraulic directional valve as set forth in claims 10 and 12, wherein the transition between the larger diameter (D7) and the smaller diameter (D8) of the axial bore (70) in the control slide valve (18) is in a space before the annular groove (58).

14. The pre-controlled hydraulic directional valve as set forth in claim 13, wherein the transition between the larger diameter (D7) and the smaller diameter (D8) of the axial bore (70) in the pilot spool (18) is spaced from the valve seat control edge (56) of the pilot spool (18) by approximately half the spacing of the annular groove (58) from the valve seat control edge (56).

15. A pre-controlled hydraulic directional valve as set forth in any one of claims 12, 13 or 14, wherein said annular groove (58) is in a pilot region of said pilot spool (18), and wherein said pilot spool (18) has pressure balancing grooves (57) on both sides of said annular groove (58).

16. Pre-controlled hydraulic directional valve according to the preceding claim, wherein the pre-controlled hydraulic directional valve comprises a valve cover (17) which is seated on the plug-in socket (15), wherein the control slide (18) projects into the valve cover (17) and the slide flange (60) and the valve cover (17) together separate the two control chambers (61, 62) from one another, and wherein, for actuating the control slide (18), pressure medium is supplied to one of the control chambers (61, 62) by the pre-control valve (11) and pressure medium exits from the other control chamber (62, 61).

Technical Field

The invention relates to a pre-controlled hydraulic directional plug-in valve, comprising a plug-in socket to be inserted into a plug-in bore of a hydraulic block, the plug-in socket having an inner bore and, toward its front end side, having a first socket section with an outer first sealing diameter and, toward its rear end side, having a third socket section with an outer second sealing diameter, which is larger than the sealing diameter in the first socket section, and having a second socket section between the first socket section and the third socket section, in the second socket section, the plug-in socket has a row of radial openings, and in the second socket section, the plug-in socket has an outer diameter in a region and in each case over a certain distance on both sides of the radial openings, the outer diameter is greater than the first sealing diameter of the outer portion and less than the second sealing diameter of the outer portion. The directional plug-in valve also has a control slide which has a slide flange for its hydraulic actuation and which is guided axially in the inner bore of the plug-in socket and with which the flow cross section between the inner bore and the radial opening can be controlled. The control slide is guided on a guide diameter at least behind a radial opening in the plug-in socket. The inner diameter of the plug-in socket is at least as large as the guide diameter in the region of the radial bore.

Background

The dimensions of the plug-in bore into which the plug-in socket is to be inserted are standardized to DIN ISO 7368 and are not as large as required depending on the nominal parameters of the directional plug-in valve. The dimensions of the row of plug-in sockets are thus predefined and can no longer be changed if standards are to be taken into account. The diameter of the plug-in bore in the region in which the first socket section of the plug-in socket and its third socket section are located after insertion of the plug-in socket is predetermined, in particular by the standard. The outer sealing diameter in the first socket section and the outer sealing diameter in the third socket section are also specified. These sealing diameters are substantially equal to the corresponding diameters of the plug-in bores.

Disclosure of Invention

The pre-controlled hydraulic directional plug-in valve with the above-described features is known from data pages RD 29137/08.13 or RD 29136/12.04 of bosch-lackloy. The directional plug-in valve can be a two-way plug-in valve or a three-way plug-in valve, wherein the two-way plug-in valve is usually designed as a seat valve and the three-way plug-in valve is usually a pure spool valve.

In such directional plug-in valves, high volumetric flows in both flow directions should be achieved.

This is achieved in that the ratio between the outer first sealing diameter and the guide diameter for the control slide lies in the range between 1.10 and 1.28.

The plug-in socket is therefore distinguished by a particularly large internal diameter, which enables a large volume flow. The control slide can be enlarged according to the large guide diameter, so that in the position in which the valve in the control slide is opened, a large flow cross section exists between the control slide and the plug-in socket. This large flow cross section allows a large volume flow without an unacceptable pressure drop across the valve. The outer diameter of the plug-in socket is determined by the standard in the region of the first front socket section and in the region of the third socket section. The two socket segments are usually provided on the outside with a circumferential annular groove into which the sealing ring is inserted. In this way, the axial working connection and the radial working connection are sealed off from the outside by the first socket section and the radial working connection is sealed off from the outside by the third socket section. The front side of the plug-in socket is used to indicate the end side which is inserted into the plug-in bore first when the plug-in socket is inserted into the plug-in bore. The concepts "front" and "rear" are brought along accordingly.

An annular channel is present between the second socket section of the plug-in socket and the wall of the plug-in bore, in order to be able to utilize all radial openings for the pressure medium flow, which are distributed over the circumference of the plug-in socket. The channel extending in the hydraulic block, which is part of the fluid path to the hydraulic consumer, starts from the annular channel.

The ratio between the outer first sealing diameter and the guide diameter is preferably in the range between 1.12 and 1.27, in particular between 1.12 and 1.25.

If the directional plug-in valve is a seat valve, the control slide with the valve seat control edge interacts with an inner step on the plug-in socket between the radial openings and the front end face in the inner bore in front of the radial openings, the control slide being guided axially on the guide diameter of the plug-in socket at least behind the radial openings and the area of the inner diameter of the plug-in socket up to the radial openings being at least as large as the guide diameter. The ratio between the outer first sealing diameter and the guide diameter is then preferably in the range between 1.10 and 1.22, in particular between 1.12 and 1.20.

The inner diameter of the plug-in socket is preferably substantially constant from the front end face up to the inner step, wherein the ratio between the first sealing diameter and the inner diameter of the plug-in socket from the front end face up to the outside of the inner step lies in the range between 1.10 and 1.30, in particular between 1.15 and 1.25. A large axial inflow channel or a large axial outflow channel is thus created for the pressure fluid inside the plug-in socket.

The second socket section of the plug-in socket advantageously has a constant outer diameter, wherein the ratio between the constant outer diameter and the guide diameter of the second socket section of the plug-in socket lies in a range between 1.15 and 1.35, in particular in a range between 1.20 and 1.30.

Advantageously, the inner step on the plug-in socket has only a very small width, since then the flow is deflected only slightly and a large inflow cross section or outflow cross section is provided for the pressure fluid. The "width of the inner step" here means the difference of half between the guide diameter and the inner diameter of the plug-in socket on the inner edge of the inner step. The inner step preferably has a width in the range between 0.8mm and 1.7mm, in particular in the range between 1mm and 1.5 mm. The width of the inner step is in particular 1mm or 1.5 mm. The value is dependent, above all, on the nominal variable of the directional plug-in valve according to the invention. The values may be, for example, 1mm for small nominal quantities NG32, NG40, NG50 and 1.5 mm for large nominal quantities NG63, NG80 and NG 100.

In order to keep the risk of splitting or breaking at the transition between the first socket section and the second socket section of the plug-in socket small, a circumferential rounded relief notch can be present on the outside at the transition from the first socket section to the second socket section, in which relief notch the outer diameter of the plug-in socket is smaller than the outer first sealing diameter.

For the throughflow of the pressure fluid, it is advantageous if the plug-in socket has a circumferential groove on the inside in the region of the radial opening. The depth of the circumferential groove is preferably 2 mm.

The pilot slide expediently has an axial bore in the fluid path between the two end sides of the pilot slide, wherein the axial bore has a first diameter from the front end side of the pilot slide in the region of the inner step of the plug-in socket via a section and a second, smaller diameter next to the first diameter, and wherein the transition between the larger diameter and the smaller diameter, viewed from the front end side, is located within a distance behind the valve seat control edge. The axial bore in the control slide serves firstly to connect the axial connection of the directional plug-in valve to the space upstream of the rear end face of the control slide and thus to establish the greatest possible pressure balance on the control slide, but also to reduce the weight of the control slide compared to a solid control slide, so that it can react more quickly to actuation. The large diameter of the axial bore from the front end of the pilot slide reduces the area of the pilot slide that is subjected to the flow forces.

Advantageously, a bevel, preferably a bevel of 30 °, is located on the edge between the axial bore of the pilot slide valve and the front end face of the pilot slide valve. Thereby further reducing the end surface of the control slide. The flow force becomes smaller.

In order to seal the rear region of the valve well against the working connection, the control slide can have an annular groove running around on the outside, in which the sealing ring is located, wherein the position of the annular groove on the control slide is such that, when the control slide rests on an inner step of the plug-in socket, the annular groove, viewed axially, is located in the region of the second socket section of the plug-in socket, the transition between the larger diameter and the smaller diameter of the axial bore in the control slide is advantageously located in a distance in front of the annular groove, so that the control slide is not too weakened in the region of the annular groove (schw ä chen).

The distance between the transition between the larger diameter and the smaller diameter of the axial bore in the control slide valve and the valve seat control edge is preferably approximately half as large as the distance between the annular groove and the sealing ring and the valve seat control edge.

The annular groove and the sealing ring can be located in a guide region of the control slide valve, wherein the control slide valve has pressure compensation grooves on both sides of the annular groove.

The pilot-controlled hydraulic directional valve according to the invention comprises, as is known per se, a valve cover which is placed on a plug-in socket. The control slide projects into the valve cover in a manner known per se and the slide flange and the cover together separate the two control chambers from one another. For actuating the control slide, pressure medium is supplied to one of the control chambers via the pilot control valve and pressure medium is removed from the other control chamber.

The drawing shows an exemplary embodiment of a pilot-controlled hydraulic directional insert valve according to the invention. The invention will now be explained in detail with the aid of the figures of the drawing.

Drawings

In the figure:

FIG. 1 shows the entire plug-in valve partly in view and partly in section;

fig. 2 shows an external view of a uncovered (blocked) plug-in socket on an enlarged scale relative to the view according to fig. 1;

fig. 3 shows the plug-in socket according to fig. 2 in a longitudinal section;

FIG. 4 shows an external view of the uncovered control slide on an enlarged scale relative to the view according to FIG. 1;

FIG. 5 shows the control slide according to FIG. 4 in a longitudinal section; and

fig. 6 is a plug-in drilling according to DIN ISO 7368.

Detailed Description

The illustrated pilot-controlled hydraulic directional plug-in valve is a two-way plug-in valve and comprises a main valve 10, a pilot valve 11, a displacement sensor (Wegaufnehmer) 12 and an integrated electronic device 13. The main valve 10 in turn has a plug-in socket (Einbaubuchse) 15 which has an internal bore 16 and which is provided for being inserted beforehand with a front end face (stimsuite) 29 into a plug-in bore 31 of a hydraulic block 30, as is shown in the cut-out in fig. 6. The plug-in socket 15 is held on a cover 17 which is screwed (verseubt) to the hydraulic block when the valve is installed. The main valve also has a control slide valve (Steuerschieber) 18, which is guided in such a way that it can move axially in the plug-in socket 15 and projects into a bore 19 of the cover 17. The bore 19, although having an extension, is nevertheless referred to herein as a bore. The borehole is stepped, wherein the borehole has, starting from a front side (seitenflacehe) 20 facing the (zugekehren) insertion borehole, a first section 21 with a large diameter, immediately following it a section 22 with a smaller diameter, and finally a section 24 which is open on a rear side 23 with a smallest diameter.

A sealing plug 25 is inserted into the section 24, through which a plunger 26 of the displacement sensor 12, which is firmly connected to the control slide 17, is guided in a sealing manner into the housing of the displacement sensor 12.

The plug-in bore 31 has two bore sections 32 and 33, the diameters D1 and D3 of which are predetermined by the standard, the fluid channel A opens axially into the (m ü den) bore section 32, the fluid channel B opens radially into the bore section 33, which is much larger than the bore section 32 and whose diameter D3 is greater than the diameter D1 of the bore section 32. correspondingly, the plug-in socket 15 has in front a first socket section 34 with an outer first sealing diameter, which is equal to the diameter D1, in the socket section 34, the plug-in socket 15 has a surrounding annular groove 35, into which the sealing ring 36 is inserted or is to be inserted, the first socket section 34 enters the bore section 32 and seals the two working connections A and B against one another on the outside of the plug-in socket 15 when it is inserted into the plug-in bore.

Furthermore, the plug-in socket 15 has a third socket section 42 at the rear, the second sealing diameter of the exterior of which is equal to the diameter D3 of the drilled-out section 33. In the socket portion 42, the plug-in socket 15 has a circumferential annular groove 38, into which the sealing ring 39 is inserted or is to be inserted. When the plug-in socket 15 is inserted into the plug-in bore, the third socket section 42 enters the bore section 33 and seals the plug-in bore 31 on the outside of the plug-in socket 15 towards the cover 17.

The third socket section 42 is much shorter than the bore section 33. Between the first socket section 34 and the third socket section 42, the plug-in socket 15 has a second socket section 37 which, after insertion, is likewise located in the region of the bore section 33, but which has a constant outer diameter D2 which is smaller than the diameter D3 of the bore section 33, so that an annular channel (Ringkanal) 43 shown in fig. 1 is formed around the socket section 37. Externally, the socket section 37 transitions conically into a third socket section 37.

The outer diameter D2 of the second socket section 37 is greater than the first sealing diameter D1 of the first socket section 34. At the transition from the first socket section 34 to the second socket section 37, there is a circumferential rounded pressure relief notch (endlastskerbe) 44 on the outside, in the low point of which the outer diameter of the plug-in socket 15 is smaller than the outer first sealing diameter D1.

At the same height in the second socket portion 37, a plurality of radial openings 45, which are distributed uniformly over the circumference of the plug-in socket 15 and are elongated in the axial direction of the plug-in socket 15 and are at a small distance from the first socket portion 34, through which a fluid connection between the annular channel 43 and the part of the inner bore 16 located in front of the openings 45 and thus between the two working connections a and B is achieved. In the region of the radial opening 45, the plug-in socket 15 has a circumferential groove 46 on the inside, the depth of which is approximately 2 mm.

Next to the groove 46, the plug-in socket 15 has a guide diameter D4 in the region of the second socket section 37 and in the region of the transition from the second socket section 37 to the conical outer portion of the third socket section 42, at which the control slide valve 18 is guided in the plug-in socket 15 and which is smaller than the first sealing diameter D1 of the first socket section 34. The ratio between the first sealing diameter D1 and the guide diameter D4 is in the range between 1.10 and 1.28. In fig. 2 and 3, the plug-in socket 15 of the direction-plug-in valve of the nominal value 40 is shown, wherein the first sealing diameter D1 is equal to 55 mm. The guide diameter D4 is currently 48 mm, so that in the exemplary embodiment the ratio between the first sealing diameter D1 and the guide diameter D4 is equal to 1.146, i.e. in the range between 1.10 and 1.28, in particular in the range between 1.12 and 1.20. The ratio may be different at other nominal quantities. The ratio can also depend on whether the directional plug-in valve is a two-way plug-in valve of the seat valve configuration (Sitzbauweise) or a two-way plug-in valve or a three-way plug-in valve of the pure spool valve configuration without a valve seat for the control spool.

Immediately behind the region with the guide diameter D4, the inner diameter of the plug-in socket 15 is slightly larger than the guide diameter D4.

The outer diameter of the second socket section 37 is kept as small as possible, so that the width of the annular channel 43 is large. In the present case, the outer diameter of the second socket section 37 is 61 mm. The ratio of the outer diameter to the inner diameter of the plug-in socket is therefore equal to 1.27 in the region of the second socket section 37. This value lies in the range between 1.15 and 1.35 and in particular in the range between 1.20 and 1.30. Other nominal variables and other embodiments are possible with other variables.

The plug-in socket 15 shown in fig. 2 and 3 is constructed in a seat valve construction. For this purpose, the inner diameter of the plug-in socket transitions before the radial opening 45 in the conical inner step 47 to the smaller inner diameter D5 of the first socket section 34. The inner diameter D5 is constant up to the front end face 29, i.e. in the region of the first socket portion 34, except for a small oblique edge. The inner diameter is as large as possible and in the present case amounts to 46 mm. The ratio between the first sealing diameter D1 and the inner diameter D5 on the first socket section 34 is therefore 1.196 and therefore lies in the range between 1.10 and 1.30, in particular between 1.15 and 1.25. The width of the inner step 47, which results from the difference between the guide diameter D4 and the inner diameter D5, which is equal to 48 mm, is therefore 1mm and therefore lies in the range between 0.8 and 1.7 mm. In the case of larger nominal variables, for example from nominal variable 63, the width of the inner step can also be 1.5 mm.

From the front end 55 with the seat control edge 56 with which the control slide can be seated (aufsitzen) on the conical inner step 47 of the plug-in socket 15, the control slide 18 has a guide diameter D6 over a certain length, which is equal to the guide diameter D4 of the plug-in socket 15, wherein the tolerances are selected such that clamping of the control slide in the inner bore 16 is precluded. The length corresponds approximately to the distance of the inner step 47 from the point at which the diameter of the inner bore 16 transitions from the guide diameter D4 to a slightly larger inner diameter in the region of the third socket section 42. In the region of the control slide valve, in which this is guided on the guide diameter D4 of the plug-in socket, a pressure compensation groove (druckausgleichsrille) 57 is located on the outside of the control slide valve 18. A circumferential annular groove 58, into which a sealing ring 59 is inserted or is to be inserted, is bored into the control slide valve 18 approximately in the center of this region (eindrehen). The bore 19 in the cover 17 is therefore sealed well internally against the working connections a and B. When the control slide valve 18 rests on the inner step 47 of the plug-in socket 15, the annular groove 58 and therefore the sealing ring 59 are located in the region of the second socket portion 37.

The control slide 18 has a slide flange 60 in a bore section 21 in the cover 17, which bore section has a diameter greater than the pilot diameters D4 and D6, by means of which two control chambers 61 and 62 are formed in the bore section 21, which are separated from one another, one of the control chambers being fluidically connected to the first connection via a fluid path in the cover 17 and the other to the second connection of the pilot control valve 11. If the pilot valve is actuated in such a way that hydraulic oil is supplied to the control chamber 61 and leaves the control chamber 62, the control slide 18 is moved in such a way that the flow cross section between the two working connections a and B is opened or enlarged. If, on the other hand, the pilot valve is actuated in such a way that hydraulic oil is supplied to the control chamber 62 and leaves the control chamber 61, the control slide 18 is moved in such a way that the flow cross section between the two working connections a and B is reduced or closed.

The control slide 18 projects beyond the bore section 21 into a bore section 22 of the bore 19 in the cover 17. The diameter of the drilling section 22 is equal to the guide diameter of the plug-in socket 15 and the control slide valve 18. The space behind the control slide valve 18 in the cover 17 is sealed well against the control chamber 62 by a sealing ring 64 inserted into an annular groove 63 of the control slide valve 18.

A central axial bore 70 of a defined length from the end face 55 of the pilot slide is introduced into the pilot slide 18, the diameter of which is as large as possible, taking into account the strength of the pilot slide, in order to make the latter lightweight. From the rear end face, a blind hole 72 is introduced into the material remaining between the blind hole 70 and the rear end face 71, said blind hole serving to fix the plunger 26 of the displacement sensor 12 to the pilot slide 18. By means of small bores 73 arranged eccentrically in the remaining material and by means of the axial bore 70, an open fluid connection is created between the spaces in front of the two end sides 55 and 71 of the control slide 18. The control slide 18 is therefore as pressure-balanced as possible.

The axial bore 70, starting from the front end face 55 of the pilot slide valve 18, has a first diameter D7 first via a certain path and then a second, smaller diameter D8. The region of the transition between the larger diameter D7 and the smaller diameter D8 is oriented axially such that, during operation, it is also located behind the radial opening 45, as viewed from the front end face 55, depending on the size of the stroke of the control slide 18. The section of the axial bore 70 with the larger diameter D7 is therefore longer. However, this section ends before the annular groove 58 at a distance therefrom, so that the control slide valve 18 is still sufficiently stable in the region of the annular groove. In the exemplary embodiment shown, the distance at the point of transition between the two diameters of the valve seat control edge 56 of the control slide 18 is approximately half as large as the distance of the annular groove 58 from the valve seat control edge. Since the control slide 18 shown does not have any fine control region upstream of the seat control edge, which is therefore formed on the front end side, the same applies to the distance of the front end side 55.

In the section of the axial bore with the larger diameter D7, the ratio between the outer diameter of the control slide and the diameter D7 is equal to 1.33. Due to the large diameter D7 of the axial bore 70 in the region of the end face 55, the flow forces acting on the control slide 18 are small.

At the edge between the axial bore 70 and the front end face 55 of the pilot slide valve is a bevel (Fase) 74, which encloses an angle of 30 ° with the axis of the pilot slide valve 18. The end side becomes further smaller. The flow forces are still becoming smaller.

List of reference numerals

10 main valve

11 pre-control valve

12 displacement sensor

13 integrated electronic device

15-plug socket

1615 inner bore

17 cover

18 control slide valve

1917 drilling holes

2017 front side

2119 section

2219 section

2317 at the rear side

2419 section(s)

25 sealing plug

2612 mandrel

2915 front end side

30 hydraulic block

31-insertion type drill hole

3231 drilling section

3331A drilling section

3415 a first socket section

3534 annular groove

36 sealing ring

3715 second socket section

3842 annular groove

39 sealing ring

42 third socket section

43 annular channel

44 pressure relief notch

45 radial opening

46 surrounding the groove

4715 inner step

5518 a front end side

5618 seat control edge

5718 pressure equalizing groove

5818 annular groove

5958 sealing ring

60 spool valve flange

61 control chamber

62 control chamber

6318 annular groove

6463 sealing ring

7018 axial drilling

7118 rear end side

72 blind hole

7318 drilling holes

7418 bevel edge

A working joint

B working joint

Diameter of D132 and seal diameter of 34

Outer diameter of D237

Diameter of D333 and sealing diameter of 42

Guide diameter of D437

Inner diameter of D534

Outer diameter, guide diameter of D618

Larger first diameter of D770

A second smaller diameter of D870.