阅读说明：本技术 用于机动车的自动变速器的液压控制装置 (Hydraulic control device for automatic transmission of motor vehicle ) 是由 M·古蔡特 T·施密特 于 2020-02-13 设计创作，主要内容包括：本发明涉及一种用于机动车的自动变速器的液压控制装置。该液压控制装置包括：阀套；阀盖,其在一端侧上部分地封闭阀套；阀芯,其在阀套内沿纵向方向被引导；壳体部件、尤其是通道板,其具有与阀套外轮廓相配的凹口。中间板可部分地遮盖阀盖并形成用于阀盖的支座。设置在阀套内的弹簧用于在初始位置中预紧阀芯。阀套与阀盖、阀芯和弹簧一起被插入到壳体部件、尤其是通道板的凹口中并且所述构件一起构成液压阀。阀套在此形成用于液压液体进入到液压阀的输入部,阀盖形成用于液压液体从液压阀的输出部。此外,壳体部件、尤其是通道板形成用于将液压液体输送至阀套的输入部的通道,中间板形成用于将液压液体从阀盖的输出部导出的通道。(The present invention relates to a hydraulic control apparatus for an automatic transmission of a motor vehicle. The hydraulic control apparatus includes: a valve housing; a valve cover partially closing the valve sleeve on one end side; a valve core guided in the longitudinal direction within the valve housing; the housing part, in particular the channel plate, has a recess adapted to the outer contour of the valve sleeve. The intermediate plate may partially cover the valve cover and form a seat for the valve cover. A spring arranged in the valve sleeve serves to pretension the valve element in the initial position. The valve sleeve together with the valve cover, the valve core and the spring is inserted into a recess of the housing part, in particular the channel plate, and the components together form the hydraulic valve. The valve sleeve forms an inlet for the hydraulic fluid into the hydraulic valve and the valve cover forms an outlet for the hydraulic fluid from the hydraulic valve. Furthermore, the housing part, in particular the channel plate, forms a channel for conveying the hydraulic fluid to the inlet of the valve sleeve, and the intermediate plate forms a channel for discharging the hydraulic fluid from the outlet of the valve cover.)

1. Hydraulic control device (4) for an automatic transmission (3) of a motor vehicle (1), the hydraulic control device (4) comprising:

a valve sleeve (12, 112, 212),

a valve cover (15, 115, 215) which partially closes the valve sleeve (12, 112, 212) on one end side (S1),

-a valve spool (13) guided in the valve housing (12, 112, 212) in a longitudinal direction (L),

a housing part (6) having a recess (8) adapted to the outer contour of the valve sleeve (12, 112, 212),

-an intermediate plate (7) partially covering the valve cover (15, 115, 215) and forming a seat for the valve cover (15, 115, 215), and

a spring (14) arranged in the valve sleeve (12, 112, 212) for biasing the valve element (13) in an initial position,

wherein the content of the first and second substances,

-the valve sleeve (12, 112, 212) together with the valve cover (15, 115, 215), the valve spool (13) and the spring (14) are inserted into the recess (8) of the housing part (6) and constitute a hydraulic valve (9, 42, 43),

-the valve housing (12, 112, 212) forms an input (19) for the entry of hydraulic liquid into the hydraulic valve (9, 42, 43),

-the valve cover (15, 115, 215) forms an output (31) for hydraulic liquid output from the hydraulic valve (9, 42, 43),

-the housing part (6) forms a channel (28) for conveying hydraulic liquid to an inlet (19) in the valve housing (12), and

-the intermediate plate (7) forms a channel (32) for conducting hydraulic liquid out of the outlet (31) of the valve cover (15).

2. The hydraulic control apparatus (4) according to claim 1,

-the recess (8) is a stepped hole having two hole steps (10, 11),

-the two hole steps (10, 11) are embodied in a manner matched to the two valve flanges (16, 17) of the valve sleeve (12, 112, 212), and

-the bore lengths (L1, L2) of the two bore steps (10, 11) are coordinated with one another such that the valve sleeve (12, 112, 212) can be inserted into the stepped bore (8) in such a way that firstly only the valve flange (16) having the larger outer diameter (DA1) comes into contact with the stepped bore (10).

3. The hydraulic control apparatus (4) according to claim 1 or 2,

-without changing the configuration of the valve sleeve (12, 112, 212) and the recess (8) in the housing part (6) and

-by modifying the spool (13) and the channel (28) for conveying hydraulic liquid

The hydraulic valve (9, 42) is provided as a volume flow control valve (9) in a first alternative and as a pressure limiting valve (42) in a second alternative.

4. The hydraulic control apparatus (4) according to any one of the preceding claims,

-without changing the configuration of the valve sleeve (12, 112, 212) and the recess (8) in the housing part (6) and

-by modifying the spool (13) and the channel (28) for conveying hydraulic liquid and

-by varying the arrangement of the springs (14) supported on the housing part (6),

in a third alternative, the hydraulic valve (43) is provided as a pressure relief valve (43).

5. The hydraulic control apparatus (4) according to any one of the preceding claims,

-the valve cover (15) is embodied as a separate component from the valve housing (12), and

the valve sleeve (12) has a rib (44) by means of which the valve cover (15) is fixed in a form-fitting manner on one end face (S1) of the valve sleeve (12).

6. The hydraulic control device (4) according to any one of claims 1-4, wherein-the valve cover (115) is implemented as a separate component from the valve housing (112), and

-the valve cover (115) is fixed on one end side (S1) of the valve sleeve (112) in a force-fitting manner by means of a press fit.

7. The hydraulic control apparatus (4) according to any one of claims 1 to 4,

the valve cover (15, 115) is embodied as a separate component from the valve housing (12, 112),

-the valve cover (15, 115) and the valve housing (12, 112) are made of plastic, and

-the valve cover (15, 115) and the valve housing (12, 112) are glued or connected to each other by friction welding.

8. The hydraulic control device (4) as claimed in any one of the preceding claims, wherein the valve cover (215) is formed by the valve sleeve (212).

9. The hydraulic control device (4) as claimed in one of the preceding claims, wherein the housing part (6) forms a stop (39) against which the valve spool (13) rests in such a way that an annular gap (40) is always present between the valve spool (13) and the valve sleeve (12, 112, 212).

10. The hydraulic control device (4) as claimed in one of the preceding claims, wherein the spring (14) exerts a return force on the valve spool (13) in such a way that the valve cover (15, 115, 215) and the valve sleeve (12, 112, 212) are sealed with respect to the intermediate plate (7) in the longitudinal direction (L) of the hydraulic valve (9, 42, 43).

11. The hydraulic control device (4) as claimed in any one of the preceding claims, wherein the hydraulic liquid fed to the hydraulic valve (9, 42, 43) exerts a force on the spool (13) such that the valve cover (15, 115, 215) and the valve sleeve (12, 112, 212) are sealed with respect to the intermediate plate (7) in the longitudinal direction (L) of the hydraulic valve (9, 42, 43).

12. Automatic transmission (3) for a motor vehicle (1), the automatic transmission (3) comprising a hydraulic control device (4) according to any one of the preceding claims.

13. Motor vehicle (1) comprising an automatic transmission (3) according to claim 12.

Technical Field

The present invention relates to a hydraulic control apparatus for an automatic transmission of a motor vehicle. The invention also relates to an automatic transmission having the hydraulic control device and a motor vehicle having the automatic transmission.

Background

Hydraulic control units for automatic transmissions of motor vehicles can have different hydraulic valves which perform different functions within the hydraulic control unit, such as volume flow control valves, pressure limiting valves and pressure reducing valves. These hydraulic valves are typically implemented as separate components and are connected to the port plate or valve plate interface of the hydraulic control device. This requires an inherent interface and installation space for the hydraulic valve in question. Furthermore, each hydraulic valve must be connected on the one hand to the channel plate and on the other hand to another element of the hydraulic control device.

Disclosure of Invention

The object of the present invention may be to provide a hydraulic control device which requires little installation space and can be produced with little assembly effort. This object is achieved by the subject matter of the independent claims. Advantageous embodiments are the subject of the dependent claims, the following description and the figures.

According to a first aspect of the present invention, a hydraulic control apparatus for an automatic transmission of a motor vehicle is provided. The hydraulic control device comprises a valve sleeve, a valve cover which partially closes the valve sleeve at one end side, and a valve core which is guided in the longitudinal direction inside the valve sleeve. The hydraulic control device also comprises a housing part with a recess adapted to the outer contour of the valve sleeve. Furthermore, an intermediate plate may be provided which partially covers the valve cover and forms a seat for the valve cover. The hydraulic control device further comprises a spring arranged in the valve sleeve and used for pre-tightening the valve core in the initial position.

The housing part can be, in particular, a channel plate or a valve plate. A "channel plate" is understood to mean an element of the hydraulic control device which comprises a plurality of channels for conducting hydraulic fluid, in particular oil. The channel plate may for example be a casting. The valve plate may also be a casting. The valve plate can be designed, for example, for receiving a valve of a hydraulic control device or for providing an interface for a valve. The hydraulic control device may include a channel plate and may also include a valve plate, wherein an intermediate plate may separate the channel plate from the valve plate. The invention is described for the most part below in connection with a channel plate, wherein these embodiments are equally applicable to other housing parts of a hydraulic control device, in particular to a valve plate, in the same sense.

According to the invention, the valve sleeve, together with the valve cover, the valve core and the spring, is inserted into a recess of the housing part, in particular of the channel plate, and forms the hydraulic valve. The valve sleeve can form an inlet for the hydraulic fluid into the hydraulic valve, and the valve cover can form an outlet for the hydraulic fluid out of the hydraulic valve. Furthermore, the housing part can form a channel for conveying hydraulic fluid to an inlet in the valve housing, and the intermediate plate can form a channel for discharging hydraulic fluid from an outlet of the valve cover.

The hydraulic valve, which is composed of a valve sleeve, a valve cover, a valve core and a spring, can be installed or fitted as a so-called "insert" in the hydraulic control device. The assembly can be carried out in such a way that there is no additional expenditure on the operating procedure, since in hydraulic control devices a series of inserts (for example sieve, check valve, balls) are normally installed, which are in the valve plate or in the channel plate. According to the invention, the hydraulic valve is designed such that it can be fitted or inserted in the simplest manner during fitting into a channel plate or a valve plate of a hydraulic control device, in particular without costly centering or pressing devices.

The recess can be embodied as a stepped bore with two bore steps. In this case, the two bore steps can be embodied in a manner matched to the two valve flanges of the valve sleeve, wherein the bore lengths of the two bore steps are matched to one another, so that the valve sleeve can be inserted into the stepped bore in such a way that firstly only the valve flange with the larger outer diameter comes into contact with the stepped bore. In other words, the step length of the stepped bore is selected such that the larger upper flange of the valve sleeve can be inserted to some extent into the existing valve seat, while the smaller lower flange of the lower part does not come into contact with the bore. In this case, the larger flange is already guided, and then the smaller flange is guided in. This makes assembly easy. In particular no threads are required.

The feature "adapted to the design" is to be understood in this context to mean that the inner diameter of the first bore step is matched to the outer diameter of the first valve collar in such a way that the first valve collar can be inserted into the first bore step. The inner diameter of the first bore step may, for example, correspond to the outer diameter of the first valve flange, taking into account tolerances. Accordingly, the inner diameter of the second bore step is matched to the outer diameter of the second valve flange, so that the second valve flange can be inserted into the second bore step. The inner diameter of the second bore step may, for example, correspond to the outer diameter of the second valve flange, taking into account tolerances.

The inner diameters of the two bore steps and the outer diameters of the two valve flanges extend in the radial direction of the hydraulic valve. In the axial direction or in the longitudinal direction of the hydraulic valve, the first bore step has a first bore length and the second bore step has a second bore length. The two bore lengths of the two bore steps can be matched to one another in such a way that the valve sleeve can be inserted into the stepped bore in such a way that, first of all, only the valve flange with the larger outer diameter is in stepped contact with the stepped bore, in particular with the first bore step of the stepped bore.

The first outer diameter of the first valve flange may be greater than the second outer diameter of the second valve flange. Accordingly, the first inner diameter of the first bore step may be greater than the second inner diameter of the second bore step. The second hole step can in particular be a hole step which projects further into the channel plate than the first hole step. In other words, the second hole step is located only within the channel plate, while the first hole step is connected with the surface of the channel plate. Thus, the valve sleeve can be inserted into the channel plate through the first bore step. First, a narrower second valve flange may be inserted into a wider first bore step. When the first, wider valve flange is inserted into the first, wider bore step, the first valve flange is then guided by the first bore step, wherein the second valve flange is not yet sunk into the second bore step, but rather is still located within the first bore step. However, guiding the first valve flange through the first hole step causes the second valve flange to be simultaneously placed in the correct position for subsequent insertion into the second hole step.

The hydraulic valve may be a volume flow regulating valve or a pressure limiting valve or a pressure reducing valve. It is possible to provide a structural group that enables different valve functions to be provided within the hydraulic control device using a plurality of identical components. In particular, the valve type described can be realized in such a way that the valve element is adapted to the respective function. In all three variants, the recess or the valve seat opening in the channel plate can be identical. The castings or channels in the channel plate for feeding hydraulic fluid to the hydraulic valves and discharging hydraulic fluid from the hydraulic valves can be adapted to the requirements of the respective valve type. The three valve types described above can be realized in particular by a change in the connection of the valve spool and the hydraulic valve in the hydraulic control device.

In this sense, in one embodiment, the hydraulic valve is provided as a volume flow control valve in the first alternative and as a pressure limiting valve in the second alternative, with a constant configuration of the recesses in the valve sleeve and the channel plate and by changing the valve core and the channel for conveying the hydraulic fluid.

In a first alternative, the valve cartridge of the volume flow control valve can have a throttle plate or throttle within the valve cartridge. When the valve slide is in the regulating position, the throttle plate or throttle can be connected to the input and output of the volume flow regulating valve. Hydraulic fluid can then be supplied to the inlet of the volume flow control valve and flow through the throttle plate or throttle, such that the pressure is reduced and a constant volume flow is discharged through the outlet. The valve element can be pretensioned in the adjustment position by a spring which causes a restoring force. The hydraulic fluid supplied to the volume flow control valve via its inlet can act on the hydraulically acting surface of the valve slide in such a way that a control force is generated which counteracts the restoring force of the spring. In this way, the valve element can be moved from the regulating position into the closed position when the pressure of the hydraulic liquid exceeds the corresponding limit value. When the valve slide is in the closed position, the inlet of the volume flow control valve is closed, so that no hydraulic fluid can be supplied to the volume flow control valve.

In a further embodiment, the hydraulic valve is provided as a pressure relief valve in a third alternative by changing the arrangement of the valve core and the channel for conveying hydraulic liquid and by a spring supported on the channel plate, with the configuration of the recess in the valve sleeve and the channel plate unchanged.

Furthermore, the valve cover and the valve sleeve can be embodied as separate or integrally connected components. Accordingly, the hydraulic component can be embodied in three-piece or four-piece. The hydraulic valve is three-piece if the valve cover and the valve sleeve are connected to one another in one piece and together form a component. Component number 2 is a spool in a three-piece embodiment, and component number 3 is a spring. The hydraulic valve is of the four-piece type when the valve cover and the valve housing are embodied as separate components. In the four-piece embodiment, component number 1 is a valve sleeve, component number 2 is a valve cap, component number 3 is a valve spool, and component number 4 is a spring.

Irrespective of whether the hydraulic valve is embodied in three-piece or four-piece, the valve cover and the valve sleeve are in particular fixedly connected to one another when the hydraulic valve is inserted into the recess of the housing part. The connection can be form-locking, force-locking or material-locking. The valve sleeve is embodied in such a way that the valve element and the spring can be inserted into the valve sleeve in a first step. In a subsequent step, the valve sleeve can be closed, in particular by fitting the cover or by deformation of the valve sleeve, in such a way that the valve core is trapped in the valve sleeve.

In this context, in one embodiment the valve cover is embodied as a separate component from the valve sleeve, wherein the valve sleeve has a rib by means of which the valve cover is fixed in a form-fitting manner on one end face of the valve sleeve. The valve sleeve and the valve cover are thus connected to one another in a form-locking manner by means of the fold. In addition, if the valve cover is embodied as a separate component from the valve sleeve, the valve cover can be fixed in a force-fitting manner on one end side of the valve sleeve by means of a press fit. Furthermore, the valve cover can be embodied as a separate component from the valve sleeve, wherein the valve cover and the valve sleeve are made of plastic. In the sense of a material-locking connection, the valve cover and the valve sleeve can be adhesively bonded to one another or connected to one another by friction welding. Furthermore, according to another embodiment, the valve cover may be formed by a valve sleeve. The valve sleeve can have a catch element in the region of the end face facing away from the cover. The catch element can be produced in particular after insertion of the valve core and the spring by bending the valve sleeve radially inwards.

In a further embodiment, the housing part forms a stop against which the valve slide can be held such that an annular gap is always present between the valve slide and the valve sleeve. The hydraulic fluid can always act on the largest possible cross section of the valve slide via the annular gap in order to exert a control force on the valve slide in this way.

The spring may exert a restoring force on the valve core such that the valve cover and the valve sleeve seal against the intermediate plate in the longitudinal direction of the hydraulic valve. This sealing is obtained in particular when the valve element of the hydraulic valve is not pressurized by the hydraulic fluid. In operation, that is to say when hydraulic fluid is conducted through the hydraulic valve, the hydraulic valve can exert a force on the valve core, so that the valve cover and the valve sleeve seal against the intermediate plate in the longitudinal direction of the hydraulic valve.

According to a second aspect of the present invention, an automatic transmission for a motor vehicle is provided. The automatic transmission includes the hydraulic control apparatus according to the first aspect of the invention.

According to a third aspect of the present invention, there is provided a motor vehicle comprising an automatic transmission according to the second aspect of the present invention.

Drawings

Embodiments of the invention are explained in detail below with the aid of a schematic partial view, wherein identical or similar elements are provided with the same reference symbols. Shown here are:

fig. 1 shows a side view of a motor vehicle with an automatic transmission, which comprises a hydraulic control device,

figure 2 shows a longitudinal section through a volume flow regulating valve for the hydraulic control device according to figure 1,

figure 3 shows a schematic circuit diagram of the volume flow regulating valve according to figure 2,

fig. 4 shows a longitudinal section through the volume flow control valve according to fig. 2, which is inserted into a part of the housing of the hydraulic control device,

fig. 5 shows a longitudinal section through the valve sleeve of the volume flow control valve according to fig. 2, wherein the valve cover of the volume flow control valve is connected to the valve sleeve by means of a fold,

fig. 6 shows a longitudinal section through an alternative valve sleeve for the volume flow control valve according to fig. 2, wherein the valve cover of the volume flow control valve is connected to the valve sleeve by a press fit,

fig. 7 shows a longitudinal section through a further valve sleeve for the volume flow control valve according to fig. 2, wherein the valve cover of the volume flow control valve is connected in one piece with the valve sleeve and is bent at the lower end side,

figure 8 shows a longitudinal section through a pressure-limiting valve for the hydraulic control device according to figure 1,

figure 9 shows a schematic circuit diagram of the pressure limiting valve according to figure 8,

FIG. 10 shows a longitudinal section through a pressure-reducing valve for the hydraulic control device according to FIG. 1, an

Fig. 11 shows a schematic circuit diagram of the pressure reducing valve according to fig. 10.

Detailed Description

Fig. 1 shows a motor vehicle 1. In the example shown, a passenger car (Pkw) is involved. The motor vehicle 1 comprises a motor 2, for example an internal combustion engine or an electric motor. The motor 2 drives the motor vehicle 1 via the automatic transmission 3. The automatic transmission 3 includes a hydraulic control device 4.

Fig. 4 shows a part of the housing 5 of the hydraulic control device 4. The housing 5 comprises housing parts, in the embodiment shown a channel plate 6 and an intermediate plate 7, which can separate the channel plate 6 from the other housing part (e.g. a valve plate). The channel plate 6 has a recess 8 into which a volume flow control valve 9 is inserted or inserted according to fig. 4.

The recess 8 may be a hole. In the embodiment shown, the recess 8 is a stepped bore. The stepped bore 8 comprises a first bore step 10 having a first bore diameter D1 in the radial direction r of the volume flow control valve 9 and a first bore length L1 in the axial direction L of the volume flow control valve 9. Furthermore, the stepped bore 8 comprises a second bore step 11 having a second bore diameter D2 in the radial direction r of the volume flow regulating valve 9 and a second bore length L2 in the axial direction L of the volume flow regulating valve 9. The first aperture D1 is larger than the second aperture D2. The first hole length L1 is greater than the second hole length L2.

As can be seen particularly well from fig. 2, the volume flow control valve 9 has a valve sleeve 12 and a valve core 13. The valve core 13 is guided in the longitudinal direction L inside the valve housing 12. Furthermore, the volume flow regulating valve 9 comprises a return element in the form of a spring 14 and a valve cover 15. For reasons of clarity, some components of the volume flow control valve 9 are provided with reference numerals only in fig. 2. Fig. 3 schematically shows the volume flow regulating valve 9. The valve sleeve 12 can be made of aluminum or plastic, for example. The valve sleeve 12 may be a turned part, for example. The valve cap 15 is fixedly connected to the valve housing 12. Examples relating to this are illustrated by fig. 5 to 7, which will be explained in detail below. The valve sleeve 12 and the valve cover 15 can also both be made of plastic and be adhesively bonded to one another or else be connected to one another by friction welding in a material-locking manner.

The valve core 13 can be adjusted back and forth in the valve housing 12 along the longitudinal axis L of the volume flow control valve 9 in axial directions x1 (first direction) and x2 (second direction) opposite to each other. The outer diameter of the valve core 13 and the inner diameter of the valve sleeve 12 are correspondingly adapted to one another in this connection. When the volume flow control valve 9 is mounted in the channel plate 6, the valve slide 13 is biased by means of a spring 14 into the control position shown in fig. 4. The spring 14 is arranged in the region of the first end side S1 of the volume flow rate control valve 9 (at the top when the volume flow rate control valve 9 is inserted into the channel plate 6). The first end side S1 faces the intermediate plate 7.

The valve housing 12 comprises a first valve flange 16 having a first outer diameter DA1 in the radial direction r of the volume flow control valve 9 and a first flange length LB1 in the axial direction L of the volume flow control valve 9. Furthermore, the valve sleeve 12 comprises a second valve flange 17 having a second outer diameter DA2 in the radial direction r of the volume flow control valve 9 and a second flange length LB2 in the axial direction L of the volume flow control valve 9. The first outer diameter DA1 is greater than the second outer diameter DA 2. The first flange length LB1 is greater than the second flange length LB 2.

The first outer diameter DA1 of the first valve flange 16 of the valve sleeve 12 is embodied to fit the first bore diameter D1 of the first bore step 10 of the channel plate 6. In particular, first outer diameter DA1 may be as large as or slightly smaller than first bore diameter D1. In this way, the first valve flange 16 can be introduced into the first bore step 10 easily and with a precise fit when the intermediate plate 7 is not yet on the channel plate 6. The ratio of the first bore length L1 of the first bore step 10 to the second bore length L2 of the second bore step 11 is selected such that firstly only the outer surface of the first valve flange 16 comes into contact with the first bore step 10, while the second valve flange 17 initially does not yet protrude into the second bore step 11 and does not yet come into contact with the second bore step 11. In other words, the larger first valve flange 16 has already been guided through the first bore step 10 before the smaller second valve flange 17 is introduced into the second bore step 11. This facilitates the assembly of the valve sleeve 12 in the channel plate 6.

At the point where the first valve flange 16 transitions to the second valve flange 17, the valve sleeve forms a step 18. In the region of the step 18, the valve sleeve 12 comprises a radial bore 19 which extends through the second valve flange 17. In the embodiment according to fig. 2, the radial holes 19 are through holes. The radial through bore 19 can serve as an inlet for the volume flow control valve 9 for hydraulic fluid, in particular oil (therefore, in the following, this radial bore 19 is also referred to as inlet). The valve slide 13 also comprises a radial through-hole 20, which in the exemplary embodiment according to fig. 2 has partially the same diameter as the through-hole 19 in the second valve flange 17. In the position of the valve slide 13 shown by way of fig. 2, the radial through-opening 20 of the valve slide 13 is aligned with the radial through-opening 19 of the second valve flange 13 of the valve sleeve 12, so that a connection exists between these two radial through- openings 19, 20.

The term "connected" is to be understood in particular to mean that the elements which are connected to one another in each case are connected to one another in a hydraulically guided manner, i.e. hydraulic fluid, in particular oil, can flow from one element to the other and vice versa, if appropriate. The term "separate" or "unconnected" is to be understood in particular to mean that the elements which are separated from one another in each case are not connected to one another in a hydraulically guided manner, i.e. that no hydraulic liquid, in particular oil, can flow from one element to the other and vice versa, if appropriate.

The radial through-hole 20 of the valve element 13 is formed as a stepped hole. The radial through-holes 20 connect mutually opposing sections of the outer surface of the valve slide 13 in the exemplary embodiment according to fig. 2. In the region of the radially outer step 33, the through-hole 20 has a larger first bore diameter 21. In the region of the radially inner step 25, the through-hole 20 has a smaller second bore diameter 22.

The valve spool 13 also includes an axial through hole 23. The axial through bore 23 extends coaxially around the longitudinal axis L of the valve spool 13. In the region of the second end side S2 (lower when the volume flow regulating valve 9 is inserted into the channel plate 6), the axial through hole 23 has a first bore diameter 24, which is located on the opposite side of the volume flow regulating valve 9 from the first end side S1. The axial through bore 23 and the radial through bore 20 intersect in their inner step 25, so that there is a hydraulic connection between the axial through bore 23 and the radial through bore 20.

In the first axial direction x1, a region is connected to the inner step 25, in which the axial through-hole 23 has the second diameter 26. The second diameter 26 of the axial through hole 23 is smaller than its first diameter 24. The second diameter 22 of the radial through hole 20 and the second diameter 26 of the axial through hole 23 may have the same diameter as in the embodiment according to fig. 2. The region of the axial through bore 23 with the smaller second bore diameter 26 fulfils the function of a throttle plate. The hydraulic fluid flowing through the radial through bore 20 decreases in pressure in the throttle disk 26 as a result of the diameter reduction there, a constant volume flow exiting from the throttle disk 26.

Fig. 4 shows that the intermediate plate 7 has a first through hole 27 and the channel plate 6 comprises a conveyor channel 28. In the assembled state, the first through-opening 27 of the intermediate plate 7 is connected to the supply duct 28 of the duct plate 6, and the supply duct 28 of the duct plate 6 is connected to the inlet 19 of the volume flow control valve 9. Hydraulic fluid can be supplied to the inlet 19 of the volume flow control valve 9 via these line sections 27, 28. The supply channel 28 comprises a first channel section 29 which extends parallel to the longitudinal axis L of the volume flow control valve 9. The second channel portion 30 of the supply channel 28 is connected to the first channel portion 29 and extends at an angle of 90 °, so that the supply channel 28 is connected to the inlet 19 of the volume flow control valve 9.

The valve cover 15 is provided on the first end side S1 of the volume flow rate adjustment valve 9. The valve cover 15 has an opening 31 which serves as an outlet for the hydraulic liquid. The intermediate plate 7 has a second through hole 32. In the assembled state, the opening 31 of the valve cover 15 of the volume flow control valve 9 is connected to the second through hole 32 of the intermediate plate 7. The hydraulic fluid fed to the inlet 19 of the volume flow control valve 9 via the first passage opening 27 and the feed channel 28 can be reduced in pressure within the volume flow control valve 9 as described below, so that a constant volume flow of the hydraulic fluid leaves the volume flow control valve 9 via the outlet 31 and is discharged via the second passage opening 32 of the intermediate plate 7. When the volume flow rate control valve 9 is inserted into the stepped bore 8, the axial through-hole 23 is closed on the opposite second end side S2 of the volume flow rate control valve 9 by the channel plate 6 (fig. 4). In this connection, the second bore step 11 is embodied as a blind bore. Therefore, no hydraulic fluid leaves the volume flow control valve 9 on the second end side S2.

When the valve slide is in the regulating position shown by fig. 4, hydraulic fluid can enter the radial through-opening 20 via the inlet 19 and flow over the radially outer step 33, which has the larger bore diameter 21. The hydraulic liquid can fill the entire radial through bore 20 and the entire axial through bore 23, building up pressure before the throttle plate 26. The hydraulic fluid then decreases in pressure in the throttle disk 26 due to the reduced diameter 22 there, so that a constant volume flow exits the throttle disk 26 in the direction of the first end side S1.

A constant volume flow of hydraulic liquid from the throttle plate 26 flows in the first axial direction x1 into the recess 34 of the valve spool 13. The recess 34 connects the valve element 13 in the axial direction L with the interior space 35 of the valve sleeve 12. The recess 34 can be embodied, for example, as an axial bore. The inner space 35 of the valve sleeve 12 is in turn connected to the opening 31 of the valve cap 15 and to the second through-opening 32 of the intermediate plate 7. A constant volume flow of hydraulic fluid from the throttle disk 26 can thus be conducted out of the volume flow control valve 9 via the recess 34, the interior space 35, the opening 31 in the valve cover 15 and via the second through opening 32 in the intermediate plate 7 and supplied downstream to a component of the automatic transmission 3, for example an annulus of a torque converter.

The spring 14 is received in a recess 34 forming a pressure surface 36. A first end of the spring 14 abuts against a pressure surface of the valve cover 15. The other end of the spring bears against a pressure surface 35 of the valve slide 13. The pressure surface 35 of the valve slide 13 extends perpendicularly to the longitudinal direction L and in the radial direction r. The spring 14 is preloaded. The spring 14 exerts a return force on the pressure surface 36. This restoring force acts in the second axial direction x2 on the pressure surface 36 of the valve slide 13, so that the valve slide 13 tends to move into the end stop position shown in fig. 2.

The actuating force acting in the first axial direction x1 on the valve slide 13 can be caused by the hydraulic fluid which is supplied to the volume flow control valve 9 via its inlet 19 as described above. The valve slide 13 forms an annular surface 37 radially on the outside and a stop surface 38 radially on the inside in the region of the second end side S2. The stop surface 38 is also annular in the illustrated embodiment. The annular surface 37 and the stop surface 38 of the valve slide 13 extend perpendicularly to the longitudinal direction L and in the radial direction r. The stop surface 38 is arranged at a distance from the annular surface 37 in the second axial direction x2 and forms a closing of the end face of the valve slide 13. The channel plate 6 forms, according to fig. 4, a stop 39 for the stop surface 38 of the valve slide 13 in the second axial direction x2 in the region of the second end side S2 of the volume flow control valve 9. The spring 14 presses the valve slide 13 with its stop face 38 against a stop 39 of the channel plate 6. The stop 39 is positioned in such a way that an annular gap 40 is always realized between the annular surface 37 of the valve slide 13 and an opposing stop surface 41 of the valve sleeve 12. As a result, hydraulic fluid can always act on the complete annular surface 37.

The hydraulic fluid can flow through the inlet 19, through the radial through openings 20, through the axial through openings 23 of the volume flow control valve 9 and through the channel formed by the channel plate to the annular surface 37 (see in particular fig. 4) and exert a pressure on the annular surface 37. The adjusting force corresponding to this pressure counteracts the restoring force of the spring 14 in the first axial direction x 1. If the adjusting force rises, the valve spool 13 tends to move in the first axial direction x1 against the restoring force of the spring 14. When the pressure of the hydraulic fluid on the annular surface 37 exceeds a limit value, the valve slide 13 closes the inlet 19, so that the hydraulic fluid no longer reaches the interior of the volume flow control valve 9. Subsequently, the actuating force drops again, so that the valve slide 13 is moved again in the axial direction x2 by the restoring force of the spring 14, the valve slide 13 releasing the inlet 19 again and a pressure or actuating force can build up again on the annular surface 37.

The spring 14 is supported on the spool 13 on one side and on the bonnet 15 on the other side in the axial direction L. The spring 14 is prestressed and exerts the above-mentioned restoring force on the valve slide 13, as a result of which the valve slide is pressed against the stop 41 in the position shown by fig. 4. Furthermore, the spring 14 presses the valve cover 15, which is fixedly connected to the valve sleeve 12, against the intermediate plate 7 by means of its pretensioning. In this way, when the volume flow rate adjustment valve 9 is inserted into the channel plate 6 and closed in the longitudinal direction L by the intermediate plate 7, the valve cover 15 is sealed with respect to the intermediate plate 7 by the spring 14.

When the hydraulic fluid exerts the above-described actuating force on the annular surface 37 of the valve slide 13, the valve slide 13 can be lifted off the stop 39 of the channel plate 6 against the restoring force of the spring 14. In this way, when the volume flow control valve 9 is inserted into the channel plate 6 and is closed in the longitudinal direction L by the intermediate plate 7, the valve cover 15 is sealed in operation with respect to the intermediate plate 7 by the pressurized hydraulic fluid.

The volume flow control valve 9 can be embodied in three parts (valve sleeve 212, valve element 13 and spring 14, wherein the valve cover 215 is connected in one piece with the valve sleeve 212) or in four parts ( valve sleeve 12 or 112, valve element 13, spring 14 and separate valve cover 15 or 115). Fig. 5 shows the valve sleeve 12 and the valve cover 15 according to fig. 2 for the four-part embodiment of the volume flow control valve 9. Fig. 6 shows an alternative valve sleeve 112 and an alternative valve cover 115 for the four-part embodiment of the volume flow control valve 9. In these exemplary embodiments, the valve sleeve 12 or 112 is embodied as a turned part, wherein the end face S2 shown in the lower part in fig. 5 and 6 forms the previously described stop surface 41, respectively. The end side S1 of the valve sleeve 12 or 112 shown in the upper part in fig. 5 and 6 respectively has an opening which is partially closed by the valve cover 15 or 115 in question. The valve core 13 may be introduced through the opening of the valve housing 12 or 112 from the first end side S1 before the valve cap 15 or 115 is assembled to the valve housing 12 or 112. Next, the valve cover 15 or 115 is assembled, so that the volume flow rate control valve 9 can be inserted into the stepped bore 8 in a preassembled manner.

Detail X in fig. 5 shows that the valve cover 15 can be connected to the valve sleeve 12 in a crimped manner, wherein the rib 44 is formed on the end side S1 of the valve sleeve 12. Fig. 6 shows an alternative embodiment of a valve sleeve 112 and a valve cover 115 for a four-part embodiment of the volume flow control valve 9. Detail Y in fig. 6 shows that the valve sleeve 112 and the valve cap 115 can be connected to one another in a friction-fit manner by means of an interference press fit. Fig. 7 shows a further alternative embodiment of a valve sleeve 212 and a valve cover 215 for a three-part embodiment of the volume flow control valve 9. Fig. 7 shows detail Z, which also shows that the inner parts (valve element 13 and spring 14) can be enclosed by a deformation on the second end side S2, wherein the valve cover 215 is connected to the valve sleeve 212 in one piece on the first end side S1. The valve slide 12 can be initially introduced into the valve sleeve 212 from the second end side S2. The valve sleeve 212 is then deformed radially inwards as shown by detail Z (catch element) in fig. 7, so that the spool 13 is caught in the valve sleeve 212. The volume flow control valve 9 can then be inserted into the stepped bore 8 in a preassembled manner.

Fig. 8 shows the valve sleeve 12, the spring 14 and the valve cover 15 according to fig. 4, which are inserted into the same stepped bore 8 of the channel plate 6 according to fig. 4. However, the valve slide 13 and the feed channel 28 in the channel plate 6 are different, and they are embodied such that a pressure limiting valve 42 according to fig. 9 is provided.

Fig. 10 shows the valve sleeve 12 and the valve cover 15 according to fig. 4 inserted into the same stepped bore 8 of the channel plate 6 according to fig. 4. However, the differences are: a valve core 13; the spring 14 is supported on the passage plate 6 instead of the valve cover 15; and a feed channel 28 in the channel plate 6. The elements 6, 13, 14 and 28 are embodied in such a way that a pressure relief valve 43 according to fig. 11 is provided.

Reference numerals

D1 first aperture

D2 second aperture

DA1 first outside diameter

DA2 second outside diameter

L1 first hole Length

L2 second hole Length

LB1 first flange Length

Second flange length of LB2

Axial direction of L volume flow regulating valve

radial direction of r volume flow regulating valve

S1 first end side

S2 second end side

x1 first axial direction

x2 second axial direction

X-shaped folding edge structure

Y interference press fit structure

Z-capture element

1 Motor vehicle

2 Motor

3 automatic transmission

4 hydraulic control device

5 casing

6 housing part

7 middle plate

8 step hole

9 volume flow regulating valve

10 first hole step

11 second hole step

12 valve sleeve

13 valve core

14 spring

15 valve cover

16 first valve flange

17 second valve flange

18 steps

19 radial through hole of second valve flange

20 radial through hole of valve core

21 smaller diameter of radial through hole

Larger diameter of 22 radial through holes

23 axial through hole of valve core

Larger diameter of 24-axis through hole

25 inner step of radial through hole

Smaller diameter of 26 axial through hole

27 first through-hole of intermediate plate

28 transfer passage

29 first channel section of a conveying channel

30 second channel section of conveying channel

31 opening of valve cover

32 second through hole of intermediate plate

33 outer step of radial through hole

34 recess of valve core

35 inner space of valve housing

36 pressure surface

37 annular surface

38 stop surface

39 stop part

40 annular gap

41 valve sleeve stop face

42 pressure limiting valve

43 pressure reducing valve

44 raised edge

112 valve sleeve

115 valve cover

212 valve sleeve

215 valve cover