EP2558755A1

EP2558755A1 - Valve arrangement

Info

Publication number: EP2558755A1
Application number: EP11714692A
Authority: EP
Inventors: Christian Spielvogel
Original assignee: Robert Bosch GmbH
Current assignee: Robert Bosch GmbH
Priority date: 2010-04-16
Filing date: 2011-03-30
Publication date: 2013-02-20
Also published as: US20150226349A1; DE102010048068A1; CN102959293A; US8985138B2; DE102010048068B4; US20130126010A1; WO2011141094A1; CN102959293B; US9441756B2

Abstract

The invention discloses a valve arrangement having at least two valves (217, 219) and having a housing which is designed as an installation cartridge (201). The valve arrangement may have for example two valves, one of which is a pressure regulator and the other of which is a delivery flow regulator. A valve arrangement of said type may for example be inserted or screwed into a variable-displacement pump, as a result of which the spatial requirement of the valve arrangement can be minimized.

Description

description

valve assembly

The invention relates to a valve arrangement according to the preamble of patent claim 1.

In prior art valve assemblies, cartridge-type housings are known that can be inserted into an opening of a hydraulic device.

DE 10 2007 044 451 A1 shows such a pressure control valve with a housing in cartridge construction, which is screwed into a connection plate of a hydrostatic piston engine.

GB 2 367 095 A likewise shows a pressure regulating valve and DE 296 20 927 IM a cartridge-type non-return valve.

A disadvantage of such valves is that only one valve is received in a cartridge.

Furthermore, it is known in the art to combine two valves in a housing. DE 101 36 416 A1 shows such a combination of pressure control and flow control valve. A housing of the two valves is formed in a flange with one-sided connections. Since the housing must be fixed to an outer surface of an associated hydraulic device, the space required is correspondingly large.

In contrast, the invention is based on the object to provide a valve arrangement with at least two valves whose space is minimized.

This object is achieved by a valve arrangement having the features of patent claim 1. The valve assembly according to the invention has a combination of at least two valves, wherein a common housing of the two valves is designed as an installation cartridge. With this compact arrangement, the space requirement of the valves is minimized.

Further advantageous embodiments of the invention are described in the dependent claims.

Preferably, each valve has a control piston movable in a valve bore.

It is particularly space-saving if the compact cartridge is used partially or completely in a hydraulic device. The device may e.g. be a variable pump. In particular, it is therefore preferred if the cartridge is screwed about its central axis in the hydraulic device.

In order to minimize the manufacturing effort, it is preferred if the valve longitudinal axes of the valve bores run parallel to the central axis.

A preferred development of the valve arrangement according to the invention has connections which are connected with different or all valve bores, so that the connections of different or all control pistons can be controlled. Thus, the manufacturing cost of the valve assembly can be further reduced, and their cartridge can be further reduced.

Depending on the design, it may be advantageous if the valve bores have different diameters.

In a particularly preferred embodiment with two valves, the valve arrangement according to the invention is a pressure-flow regulator for a variable displacement pump. In this case, further connections are provided on the outer circumference of the installation cartridge or on the front side next to a connection for a load-signaling line.

For screwing in the cartridge, a device for transmitting torque is preferred, which within an end face of the cartridge is arranged. Thus, since devices for transmitting torque at the outer edge and the outer circumference of the cartridge are avoided, the diameter of the cartridge and in particular that of a receptacle for the cartridge to the hydraulic device are minimized.

In this case, at least one circular-cylindrical section, which is at a distance from the central axis, is preferred, on which or within the circumference of which a contact surface for a tool is formed.

If the circular cylindrical section forms an eccentric circular cylindrical hole, the cartridge is designed as an eccentric hole screw.

In another preferred variant, an adjusting screw is screwed into an associated valve bore and serves to set a parameter (eg spring tension) of the corresponding valve. In this case, six circular-cylindrical sections are provided in each case between its edges on a hexagon socket of the screw. Thus, six attack surfaces for the tool for screwing the cartridge are integrated in the hexagon socket, whereby a double function is given to the screw.

In another variant with minimal effort for the circular cylindrical sections, these are arranged in the valve holes.

As a preferred supplement to the valve arrangement according to the invention, a special key is proposed as a tool, which has at least one projection with a circular-cylindrical section. This can be brought into contact with at least one associated circular cylindrical portion of the cartridge or inserted into the hole. In the variant with the hexagon socket, the projection of the tool is brought into contact with six circular-cylindrical sections.

The valve holes and / or the eccentric holes may be formed as blind holes. The mounting cartridge can have a two-flat with two flat sections for screwing in alternatively or in addition to the circular cylindrical sections.

As a simple backup for the control piston against falling out a arranged approximately transversely to the valve holes stop pin is preferred by the way the control piston is limited in the valve holes.

Manufacturing technology, it is simple when the stop pin is pressed into a transverse bore of the cartridge.

In the following, various embodiments of the invention will be described in detail with reference to FIGS. Show it:

Figure 1 shows a first embodiment of a valve assembly according to the invention in a perspective view;

Figure 2 shows a special key to the first embodiment of the valve assembly according to the invention in a perspective view;

Figure 3 shows the first embodiment of the valve assembly according to the invention in a sectional view;

4 shows a second embodiment of a valve arrangement according to the invention in a perspective view;

Figure 5 shows a detail of the second embodiment of the valve assembly according to the invention in a sectional view;

FIG. 6 shows a hydraulic circuit diagram of a third exemplary embodiment of a valve arrangement according to the invention with a variable displacement pump;

Figure 7 shows the third embodiment of the valve assembly according to the invention in a perspective view; Figure 8 shows a first variant of the third embodiment in a sectional view;

9 shows a second variant of the third embodiment of a valve arrangement according to the invention in a sectional view; and

FIG. 10 shows the second variant of the third exemplary embodiment according to FIG. 9 in a view;

Figure 1 shows a first embodiment of a valve assembly according to the invention in a perspective view. A housing of the valve assembly is designed as a cartridge 1, which can be screwed into an adjustable pump not shown in detail. The built-in cartridge 1 is rotated about its central axis 6. On an outer periphery of the cartridge 1 different connectors are arranged, which are explained with reference to Figure 3. These connections are in pressure fluid connections with two different valves, which are arranged together in the cartridge 1.

Each valve has a valve bore 20, 22, which are shown in Figure 3, and of which in Figure 1, the end-side arranged end portions can be seen. Thus, the front side corresponding holes 2, 4 are formed, which are spaced from each other to the central axis 6 of the cartridge 1 are arranged diametrically opposite each other.

Furthermore, additional circular small diameter circular recesses or holes 8, 10 are arranged on the front side of the cartridge 1, which are diametrically opposite to the central axis 6 and offset from the holes 2, 4 by 90 degrees. The distance of the axis of the respective hole 8, 10 from the central axis 6 is greater than the distance of the respective hole 2, 4th

Figure 2 shows a tool or a special key 12, which has two projections 14, 6 and a handle 8. Each projection 14, 16 has a circular cylindrical outer surface and a diameter which is slightly smaller than the diameter of the two holes 2, 4 of the cartridge (see Figure 1). The two projections 14, 16 in this case have a distance from each other, that of the two holes 2, 4 corresponds. Thus, the two projections 14, 16 can be inserted into the holes 2, 4 of the cartridge 1, and then the cartridge 1 can be screwed via the handle 8 in the (not shown) variable.

Alternatively, the two holes 8 and 10 may be used to screw in the cartridge 1, e.g. if damage to the holes 2, 4 is to be feared. Corresponding to the other hole size and the other center distance, the special key must then also be modified relative to that shown in FIG.

In this first embodiment, the outer diameter of the mounting cartridge 1 is minimal since no torque transmitting device (e.g., an external hexagon) has to be mounted on its outer periphery. In addition, the mounting cartridge 1 of the first embodiment is screwed into the variable displacement pump, that the end face of the cartridge 1 is approximately on a plane with the corresponding surface of the variable. Thus, the required space of the valve assembly according to the invention is minimal.

Figure 3 shows the first embodiment of the valve assembly according to the invention in a sectional view. In principle, a control piston 24, 26 is slidably received in each valve bore 20, 22 in a comparable manner. They control the pressure fluid connections of three ports 28, 30, 32, which are arranged on the circumference of the cartridge 1 and are arranged along their longitudinal axis 6 spaced from each other.

In this case, the control piston 24, 26 on the one hand by the pressure of the terminal 32 and on the other hand acted upon by the force of a respective spring 34, 36.

The bias of the springs 34, 36 is adjustable via a respective adjusting screw 38, 40, which is screwed into a region of the respective valve bore 20, 22, which is adjacent to the respective end portion or hole 2, 4 is arranged. The spring chamber on the control piston 26 is open via a bore 35 to the outside. About this bore 35, the spring chamber and thus the control piston 26 of a control pressure, for. From the highest load pressure of all at the same time from a pump where the valve is located, supplied to powered hydraulic consumers. The spring chamber with the spring 34 is connected via a groove or flattening 37 on the control piston 24 to the terminal 28.

FIG. 4 shows a second exemplary embodiment of a valve arrangement according to the invention in a perspective view. An essential difference of Einschraubpatrone 101 against Einschraubpatrone 1 of the first embodiment is that its length is slightly shortened. Instead of the holes 2, 4 according to the first embodiment, special recesses are provided on two setscrews 138, 140. Each recess has, on the one hand, a conventional internal hexagon, which serves to adjust the respective adjusting screw 138, 140, and, on the other hand, six integrated circular cylindrical sections 102, 104. These are each arranged such that together they form sections of a circular cylinder. In each of these circular cylinder can be a projection of a tool (not shown) used, which is similar to the tool 12 of Figure 2. Thus, the valve assembly or the cartridge 101 according to Figure 4 in the manner in the manner (not shown) screw in or unscrew from the variable displacement, which was explained with reference to the first embodiment.

Figure 5 shows a detail of the second embodiment of the valve assembly according to the invention in a sectional view. The (only partially) illustrated springs 34, 36 and the (in Figure 5) right adjoining part of the valve assembly correspond to those of the first embodiment shown in FIG. 3

6 shows a hydraulic circuit diagram of a third exemplary embodiment of a valve arrangement 203 according to the invention with a variable displacement pump 205. The circuit diagram of the valve arrangement 203 applies to the second variant shown in FIGS. 9 and 10 and largely to the first variants of the third shown in FIGS. 7 and 8 embodiment. A swivel angle of the variable displacement pump 205 can be reduced or reduced via a control cylinder 207. This is done via an increase in pressure at the control pressure port A of the variable displacement pump 205 and the valve assembly 203. On the other hand, the pivot angle of the variable displacement 205 can be increased via a further actuating cylinder 209. For this purpose, a spring 21 1 of the actuating cylinder 209 and a pressure increase at the control pressure port P of the adjusting Pump 205 and the valve assembly 203 in the direction of increasing the pivot angle. The pressure or the flow rate at a working line 213 is regulated via the swivel angle set in this way.

Furthermore, the valve arrangement 203 and the variable displacement pump 205 have a common tank connection T. In addition, the valve arrangement 203 has a load reporting connection LS, via which the highest working pressure is reported by a plurality of consumers supplied by the variable displacement pump 205 via the working line 213.

The valve assembly 203 has a pressure control valve 217 and a flow control valve 219. Both valves 217, 219 are designed as proportionally adjustable 3/2-way valves and have an adjustable spring 234, 236 in the direction of the basic position of a respective control piston shown in FIG Valves 217, 219 acts. In these two basic positions of the actuating cylinder 207 is relieved via the control pressure port A, via the two valves 217, 219 and a tank line 221 to the tank T, so that the pivot angle of the variable displacement 205 is set to maximum. Also in the direction of the illustrated basic position of the flow control valve 219 acts on the load-signaling connection LS applied prescribed control pressure.

On the control piston of the valves 217, 219 continues to act on the port P and the control pressure line 215, the pump pressure in the working line 213. Thus, with increasing pump pressure of the working line 213, the valves 217, 219 set such that increasingly pump pressure on the control pressure port P and the Control pressure line 215 connected to the control pressure port A and thus the variable displacement pump 205 is pivoted back.

Figure 7 shows both variants of the third embodiment of the valve assembly 203 according to the invention (see Figure 6) in a perspective view. The valve assembly 203 has a cartridge 201 to which the three pressure ports P, A and T are arranged. The control pressure port P is provided on the front side for the pump pressure, wherein each valve 217, 219 (see FIG. Furthermore, at the periphery of the control pressure port A for adjusting the

Pivoting angle of the variable displacement pump 205 and the tank port T arranged. Adjacent to the control pressure port P is provided in the cartridge 201 a continuous transverse bore 223, which is explained with reference to Figure 8.

In order to screw in the installation cartridge 201, in this third exemplary embodiment a two-facet is provided, of which only one planar section 225a is shown in FIG.

FIG. 8 shows the third exemplary embodiment of the valve arrangement according to the invention according to FIGS. 6 and 7 in a first variant. In the sectional view, a control piston 224 of the flow control valve 219 and a control piston 226 of the pressure control valve 217 are shown. The control pistons 224, 226 are biased on the one hand via a substantially flat spring plate 227, 229 of the springs 234, 236 (in Figure 8) to the left and on the other hand via the voltage applied to the control pressure port P control pressure (in Figure 8) to the right in their switching positions proportional displaceable. The movement of the control pistons 224, 226 (in FIG. 8) is delimited to the left by a stop pin 231, which is pressed into the continuous transverse bore 223.

The movement of the control pistons 224, 226 and the associated spring plate 227, 229 (in Figure 8) to the right against the force of the springs 234, 236 is limited by respective cylindrical stop pins 233, 235 which are parallel to a central axis 206 of the cartridge 201 inside the respective spring 234, 236 are received without further fixation. In this case, the springs 234, 235 are each supported on a disk 237, 239, which are each supported via a spacer sleeve 241, 243 on a respective tapered sleeve 245, 247. The two conical sleeves 245, 247 are fixed in the respective valve bore 220, 222 by friction. For this purpose, the conical sleeves 245, 247 frustoconical inner recesses into which corresponding truncated cones 249, 251 are pressed. The pressing was done during assembly of the cartridge 201 by moving or pulling the truncated cones 249, 251 in the associated tapered sleeves 245, 247 (in Figure 8) to the right.

Between the (in FIG. 8) right or outer end section of the installation cartridge 201 and the load-signaling connection LS, and between the load-signaling connection LS and the tank connection T, as well as between the tank connection T and control pressure Connection A, and between the control pressure port A and the control pressure connection P is in each case a sealing ring 253 disposed on the outer circumference of the cartridge 201.

A spring chamber of the flow control valve 219 is connected via a transverse bore to the load-signaling connection LS, while a spring chamber of the pressure control valve 217 is connected to the tank connection T via a pressure medium connection formed between the control piston 226 and the valve bore 222 and via a transverse bore section.

By the basic positions of the control pistons 224, 226 shown in FIG. 8, connections between the control pressure connections A and P are shut off by a respective piston collar of the two control pistons 224, 226, while the control pressure connection A flows through a pressure medium connection formed between the control piston 224 and the valve bore 220 and further connected via two transverse bore sections with the tank connection T and thus relieved to the tank. By pressurizing the control pressure ports P, the two control pistons 224, 226 respectively against the force of the associated spring 234, 236 (in Figure 8) displaced to the right, both valves 2 7, 219 a connection from the control pressure port P to

Open control pressure port A. Thus, the variable displacement pump 205 is pivoted back, so that the pressure and / or the flow rate in the working line 213 are reduced.

Figure 9 shows a second variant of the third embodiment of a valve assembly according to the invention in a sectional view. In the following, only the differences of this second variant to the first variant according to FIG. 8 will be discussed.

Between the outer periphery of the cartridge 301 and the pressure medium connection formed between the valve bore 320 and the control piston 224 of the flow control valve 319, a transverse bore 331 is provided, which represents a throttled connection between the pressure medium connection and the tank port T of the valve arrangement according to the invention due to their small diameter. Spring plates 327, 329 are each integrally formed with a stop pin, the effect of which coincides with that of the stop pins 233, 235 of the first variant according to Figure 8.

Set screws 338, 340 are screwed into the valve holes 320, 322 via a respective hexagon socket and thus serve to adjust the respective bias of the springs 234, 236. The screws 338, 340 are fixed with respective lock screws 333, 335, which are also in the respective valve bore 320, 322 are screwed. The lock screws 333, 335 each have a continuous hexagon socket, which is larger than the respective hexagon socket of the screws 338, 340th

Furthermore, a retaining ring 337, 339 is inserted into each valve bore 320, 322, so that the screws 338, 340 and their counter-screws 333, 335 are secured against falling out and in particular against pressurized falling out.

Finally, the second variant of the third exemplary embodiment according to FIG. 9 between the respective spring 234, 236 and the associated adjusting screw 338, 340 has an intermediate piece with sealing ring 341, 343 for sealing, in particular, the pressure chamber of the delivery flow control valve 319 which is acted upon by load-indicating pressure with respect to the environment.

FIG. 10 shows the second variant of the third exemplary embodiment according to FIG. 9 in an end view. The following features can be seen, leading to a compact construction of the second variant of the third embodiment of the cartridge 301 according to the invention: The two-flat, consisting of the two parallel planar sections 325 a, 325 b offers the possibility of a (not shown) special tool in plant to bring and screw the cartridge 301 into or out. The stepped sizes on the one hand of the hexagon socket of the countersunk screws 333, 335 and on the other hand the set screws 338, 340, which are arranged in the valve holes 320, 322 simultaneously reachable, also contribute to a small space requirement of the two combined valves 317, 319 at. Notwithstanding the first embodiment according to Figures 1 and 3, only the two of the valve holes 20, 22 formed holes 2, 4 or only the two smaller holes 8, 10 may be arranged on the front side of the cartridge 1.

Notwithstanding the first variant of the third embodiment according to FIGS. 7 and 8, the two valve bores 220, 222 can be used as a device for torque transmission as an alternative to the biface, of which only one planar section 225a is shown in FIG. 7, so that the installation cartridge 201 can be screwed into the variable displacement pump via a special tool according to FIG.

Deviating from the first variant of the third embodiment according to FIG. 8, sealing rings according to the sealing rings 341, 343 shown in FIG. 9 can also be provided on the discs 237, 239.

Deviating from the first variant of the third embodiment according to FIG. 8, a transverse bore according to the transverse bore 331 shown in FIGS. 6 and 9 can also be provided on the built-in cartridge 201 to form a throttle.

Disclosed is a valve arrangement with at least two valves and with a housing which is designed as a built-in cartridge. The valve assembly may e.g. have two valves, one of which is a pressure regulator and the other is a flow regulator. Such a valve arrangement may e.g. be used or screwed into a variable displacement pump, whereby the space requirement of the valve assembly can be minimized.

Claims

claims

1. Valve arrangement with at least two valves (217, 219, 317, 319), characterized in that a housing of the valve arrangement is designed as an installation cartridge (1, 101, 201, 301).

2. Valve arrangement according to claim 1, wherein each valve one in one

Valve bore (20, 22, 220, 222, 320, 322) movable control piston (24, 26, 224, 226) has.

3. Valve arrangement according to claim 1 or 2, wherein the built-in cartridge about its central axis (6; 206) can be screwed into a hydraulic device.

4. Valve arrangement according to claim 3, wherein each valve bore (20,22;

220, 222; 320, 322) has a longitudinal valve axis which is parallel to the central axis (6, 206).

5. Valve arrangement according to claim 4, wherein the valve longitudinal axes have equal distances from the central axis (6, 206).

6. Valve arrangement according to one of the claims 3 to 5 with connections (28, 30, 32, P, A, T, LS) which are connected to at least two valve bores (20, 22, 220, 222, 320, 322).

7. Valve arrangement according to one of the claims 3 to 6, wherein the valve bores (220, 222, 320, 322) have different diameters.

8. Valve arrangement according to one of the preceding claims, which is a screwed into a variable displacement pressure-flow regulator (217, 219, 317, 319).

9. Valve arrangement according to one of the preceding claims with a device for transmitting torque (2, 4, 8, 10, 102, 104, 202, 204; 225a; 325a, 325b) disposed within an end surface of the cartridge.

10. Valve arrangement according to claim 9 with at least one of the central axis (6, 206) spaced circular cylindrical portion (2, 4, 8, 10, 102, 104, 202, 204), on which an engagement surface for a tool (12) is formed ,

11. Valve arrangement according to claim 10, wherein the circular cylindrical portion forms a circular cylindrical hole (2, 4, 8, 10, 202, 204).

12. Valve arrangement according to claim 10 with six circular cylindrical sections (102, 104) which are arranged on a hexagon socket of a set screw (138, 140) which is screwed into a valve bore.

13. Valve arrangement according to claim 10 or 11, wherein the circular cylindrical portion (2, 4, 202, 204) on a valve bore (20, 22, 220, 222) is arranged.

14. Valve arrangement according to one of the claims 10 to 13, wherein the tool (12) has at least one projection (14, 16) with a circular cylindrical portion which in abutment with at least one associated circular cylindrical portion (2, 4, 202, 204) of the Installation cartridge (1, 201) can be brought.

15. Valve arrangement according to one of the claims 11 to 14, wherein the valve bores (20, 22) and / or the holes (8, 10) are formed as blind holes.

16. Valve arrangement according to one of the preceding claims, wherein the built-in cartridge (201, 301) has a Zweiflach (225a, 325a, 325b).

17. Valve arrangement according to one of the preceding claims, wherein approximately transversely to the valve bores (220, 222, 320, 322) a stop pin (231) is arranged.

18. Valve arrangement according to claim 17, wherein the stop pin (231) is pressed into a transverse bore (223) of the installation cartridge (201, 301).