KR20020021147A - Hydraulic aggregate - Google Patents

Abstract

The present invention relates to an anti-skid brake device comprising a noise damping chamber (6) integrated with a pump bore (3), wherein a brake pressure generator port (THZ) and a noise damping chamber (6) are introduced into the pump bore (3). Hydraulically connected via a pressure fluid channel 3'opened radially or tangentially, and into a valve receiving bore 2 of the first valve row X of the receiving member 1 which receives the inlet valve. Connected.

Description

Hydraulic Aggregate {HYDRAULIC AGGREGATE}

Aggregates of the above kind are disclosed in WO 91/16220. This publication discloses an arrangement of noise damping chambers parallel to the low pressure accumulator bores, which are aligned together in a row on the side of the pump bore. The pressure fluid channel for the brake pressure generator port in the block-like receiving member extends through the valve receiving bore provided for the inlet valve and laterally past the pump bore to the bottom of the noise damping chamber. For each brake circuit, another vertical pressure fluid channel connecting the pump bore exclusively to the noise damping chamber extends parallel to each pressure fluid channel opening into the noise damping chamber.

As a result, in order to be able to realize the required noise damping chamber and the low pressure accumulator bore, the block has a block-type structure with a significantly different edge length, out of its original shape. On the other hand, there is a need to remove large machining clearances from the blocks required for various drilling operations in different directions. Therefore, a precise method is needed, especially to produce the noise damping chamber and the necessary pressure fluid channels. Furthermore, in order to select-split the valve row, the connection of a pipe system that separates on three sides of the receiving member. In order to achieve the pattern, it is necessary to locate the wheel brake ports on both sides of the block-shaped receiving member. This requires more space and increases the number of assembly steps required.

The invention relates to a hydraulic assembly of a sliding-controlled brake system according to the preamble of claim 1.

1A is a perspective view showing the configuration of a bore in a housing using a pressure fluid channel that is exclusively vertically opened into a rectangular receiving member of the hydraulic assembly.

FIG. 1B is a cross-sectional view of the receiving member according to FIG. 1A seen from the top of the pump bore. FIG.

FIG. 2 is a perspective view of another embodiment of a hydraulic assembly having a pressure fluid channel opening vertically across into a block-shaped receiving member. FIG.

FIG. 3 is a perspective view of a block-shaped hydraulic assembly having a connection pattern for the modified brake pressure generator port and the wheel brake port in comparison with FIGS. 1 and 2.

* Explanation of symbols for main parts of the drawings

1: accommodation member 2: valve accommodation bore

3: Pump Bore 3 ': Pressure Fluid Channel

4: Motor accommodating bore 4 ': Leakage bore

5: low pressure accumulator bore 5 ': pump suction channel

5 ": Return channel 6: Noise damping room

7: blocking member 8: through bore

9: membrane member 10: stepped portion

X: 1st valve row Y: 2nd valve row

THZ: Brake Pressure Generation Port

HL, HR, VR, VL: Wheel Brake Port

In view of the foregoing, the present invention is to produce a hydraulic assembly of the above-described kind that can be manufactured as small as possible and inexpensively. It is a particular object of the present invention to provide a connection of a brake pressure generator port of a noise damping chamber, a hydraulic connection of a second valve row and a pump bore receiving an outlet valve along the noise damping chamber, and a low pressure accumulator via a pump bore. It is to reduce the manufacturing effort required to connect to the noise damping chamber.

This object is achieved by a hydraulic assembly having the features described in claim 1.

Other features, advantages and possible applications of the invention will be described by the description of several embodiments.

FIG. 1A shows a hydraulic assembly of a sliding-controlled brake system, which assembly comprises an inlet valve and an outlet valve in a plurality of valve receiving bores 2 of a first valve row X and a second valve row Y. FIG. And a block-shaped receiving member (1) for receiving the two valve rows (X, Y) while facing across the direction in which the valve receiving bore (2) opens into the receiving member (1). And a pump bore 3 external to the.

In addition, a motor receiving bore 4 which opens vertically with the pump bore 3 between half of the bore length is arranged outside of the two valve rows X, Y. In addition, a low pressure accumulator bore 5 is arranged outside the two valve rows X, Y in the receiving member 1, which bore 5 has a symmetric axis of the valve receiving bore 2 and a pump bore ( It is perpendicular to the longitudinal axis of 3) and directed into the receiving member 1. Several pressure fluid channels 2 ', 3', 5 'connecting the valve receiving bore 2, the pump bore 3, and the low pressure accumulator bore 5 are provided with two It ensures a connection between the brake pressure generator port (THZ) and the four wheel brake ports (HR, HL, VR, VL). In addition, two hollow cylindrical noise damping chambers 6 are provided in the pump bore 3 and are opened into the receiving member 1 by means of a pressure fluid channel 3 'extending transverse to the pump axis. It is connected to the brake pressure generator port (THZ). According to the invention, therefore, the noise damping chamber 6 is integrally formed with the pump bore 3, and the brake pressure generator port THZ is connected with the noise damping chamber 6 by the pressure fluid channel 3 ′. The pressure fluid channel opens radially, preferably tangentially, into the pump bore 3 downstream of the pump pressure valve. The pressure fluid channel 3 ′ comprises a respective branch line leading to the valve receiving bore 2 of the first valve row X which receives the inlet valve. Noise damping chamber so that the noise damping chamber 6 and the pump bore 3 are preferably closed while keeping airtight with respect to the pressure fluid by the closing member 7 inserted in the two sides of the receiving member 1 from the outside. (6) It is arranged in the radial direction at each end of this pump bore (3). The pump bore 3, which penetrates the receiving member 1 perpendicular to the low pressure accumulator bore 5, is provided between the bore portion and the noise damping chamber 6 provided for the two pump pistons on both sides of the radial piston pump. In the region of, it includes a stepped portion 10 (shown explicitly in FIG. 1B). The pump suction channel 5 ′ opens into the step 10 in the direction of the low pressure accumulator bore 5. The combination of the receiving bore for the pump suction valve (return check valve) respectively fitted to the bottom of the low pressure accumulator bore 5 and the pump suction channel by milling into the pump bore 3, in particular in a space-saving manner 5 'is provided. The milling operation is in each case achieved by introducing a peripheral milling tool into the pump bore 3, which is only a few layers from the pump wall in the direction of the receiving bore arranged in the low pressure accumulator bore 5. Should be removed. This eliminates the deburring work previously required due to drilling operations in this area, and also eliminates the need for precisely machined pump suction channels. Instead, the pump channel 5 'can be very short due to the receiving bore for the pump intake valve encountering the milled slot of the pump bore in the opposite direction. Also, in order to minimize surface wear in the pump bore 3 due to the movement of the piston in the radial piston pump, the pump bore 3 has an axial offset on both sides of the motor receiving bore 4. Have

The second valve row Y is the valve receiving bore 2 for the outlet valve optimally arranged between the pump bore 3 and the first valve row X exclusively including the valve receiving bore 2 for the inlet valve. ) Exclusively. As a result, the pressure fluid channel 2 'between the two valve rows X, Y becomes particularly short and straight, and through the return channel 5' the valve row Y and the low pressure accumulator bore 5 Very preferably connected. The pump suction channel 5 'arranged between the pump bore 3 and the low pressure accumulator bore 5 is very short and also very space-saving due to the arrangement of the respective receiving bores in the block as described above. Therefore, the non-return valve (pump intake valve) which is deflected and closed in the direction of the low pressure accumulator bore 5 can be optimally positioned with minimal structural change.

Likewise, the wheel brake ports HR, HL leading to the pressure fluid channel 2 'are arranged on the upper surface of the receiving member 1 parallel to the motor receiving bore 4, which is advantageous in assembly. This arrangement allows several pipelines to be screwed next to the motor housing which is flanged to the motor receiving bore 4 in an easily accessible manner without any problems.

The other through bore 8 is arranged in the intermediate position between the two valve rows X, Y in the receiving member 1. Due to this condition, in order to connect the electric plug protruding from the motor housing to the valve control device mounted on the lower part of the receiving member 1 for the purpose of electrical contact, the plug is connected at the top of the block-shaped receiving member 1. It is possible to guide down to the shortest distance. The valve control device further includes control electronics for driving the electric motor integrated with the motor housing.

FIG. 1A shows the bore selected in the block of the receiving member 1 by means of pressure fluid channels 2 ', 3', 5 ', 5 "arranged exclusively perpendicular to the face of the receiving member 1; The arrangement of the bores in the block is such that the pressure fluid channel 2 'provided for the valve rows X, Y is only closed on the side of the receiving member 1 by the ball. Optimized to mean that it must be closed by a suitable sealing plug, on the contrary, the pressure fluid channels 3 ', 5' are very preferably selected so that the aforementioned sealing plug is removed. The pressure fluid channel 3 'connecting 6) to the brake pressure generator port THZ passes through the brake pressure generator port THZ as a straight blind end bore to the noise damping chamber 6. Radially or tangentially Likewise, the pump suction channel 5 ′ and the backflow prevention channel 5 ″ connected to the second valve row Y are blind ends from the hydraulic assembly to the low pressure accumulator bore 5 for each brake circuit. Provided by the bore, the latter being closed by the low pressure accumulator cover after the receipt of the low pressure accumulator piston and the piston return spring.

Direct placement of the pump bore 3 between the low pressure accumulator bore 5 and the second valve row Y, as a result of which the pump bore via the low pressure accumulator 5, in addition to the shortened pressure fluid path (3) The gap space between the normally closed outlet valves of the second valve row Y to the furnace is optimized, which simplifies the discharge and filling process required for the initial filling of the hydraulic assembly.

FIG. 1B is a sectional view from the height of the pump bore 3 of the receiving member 1 which can be seen from FIG. 1A to illustrate the very short pump suction channel 5 ′. Compared with the low compressor accumulator bore 5 and the valve receiving bore 2 of the second valve row Y arranged in each of the pump bore 3, the noise damping chamber 6 has a pump bore integrated therein. It can be seen that the length of (3) is very short. Only two bore ends are required to place the noise damping chamber 6 at the outer end of the pump bore 3, which is pumped in the direction of the low pressure accumulator bore 5 by a peripheral milling tool. (5 ') is produced. Moreover, in FIG. 1B the leak channel 4 ′ is located adjacent to the motor receiving bore 4 and penetrates the receiving member 1 in the direction of the valve control device disposed below the hydraulic assembly, so that the pump The leaking fluid moving from the bore 3 to the motor receiving bore 4 can be absorbed and stored in the fluid-tight housing of the valve control device.

In the embodiment of FIG. 2, which differs from the above-described embodiment according to FIGS. 1A and 1B, the configuration of the bore in the block is shown, which configuration of the bore retains the basic structure according to the invention described above, It does not require the configuration of separate channel closing means for the pressure fluid channel 2 'in the region of the ball-type closing member or the two valve rows X, Y mentioned. This allows the valve receiving bore to meet at acute angle with the receiving member 1 the pressure fluid channel 2 'of the first valve row X for each brake circuit from the bottom of the receiving member 1 as shown in the figure. Extending through (2) and thus forming in pairs, respectively, to achieve the required pressure fluid connection between each pair of inlet valves per each brake circuit in the first valve row (X). . As disclosed in FIG. 1A, the ball-type closed configuration of the pressure fluid channel 2 ′ in the second valve row Y provides a pressure fluid channel 2 ′ in the second valve row Y for each brake circuit. ) Can be avoided by connecting the valve receiving bore 2 of the corresponding brake circuit via the associated low pressure accumulator bore 5. For this purpose two return channels 5 "in each low pressure accumulator bore 5 preferably extend directly to the valve receiving bore 2 of the split-up brake circuit, said bore 2 Are combined in pairs for each valve train Y. Thus, the bore shown in FIG. 1A is such that the pressure fluid channels 2 'of the two valve trains X, Y can no longer be additionally closed externally. The lateral configuration of is changed in the direction of two valve rows (X, Y).

In all of the above-described embodiments of the present invention (FIGS. 1A, 1B, 2), each pressure fluid channel 3 ′ connecting the brake pressure generator port THZ to the noise damping chamber 6 is adapted for noise damping. In order to improve, the membrane member 9 is inserted into the pressure fluid channel 3 'via the brake pressure generator port THZ. The membrane member 9 has two valve rows in such a way that the membrane member 9 has no throttling effect on the upstream branch line of the pressure fluid channel 3 'leading to the inlet valve of the first valve row X. It is located in the pressure fluid channel 3 'extending across this valve row between (X, Y).

In contrast, in FIG. 3 the membrane member 9 is inserted from the opposite direction to the extension of the pressure fluid channel 3 ′ which passes along the side of the low pressure accumulator bore 5, which inserts the associated pressure fluid channel 2 ′. , 3 ') due to the modified connection pattern of the inlet of the brake pressure generator port THZ and the wheel brake ports VL, VR, HR, HL. Now, due to the arrangement of the brake pressure generator ports THZ offset with respect to the channel longitudinal axis, the pressure fluid channel 3 ′ in each case has a pump bore 3 or noise from the side comprising the low pressure accumulator bore 5. A first valve row X is reached across the damping chamber 6. In other respects, the configuration of the bore in the block corresponds to the embodiment of the present invention according to Figs. 1A and 1B in all basic characteristics.

Claims (8)

As a hydraulic assembly for a sliding-controlled brake system, A receiving member for receiving the inlet and outlet valves in several valve receiving bores of the first and second valve rows, A pump bore disposed outside said two valve rows in said receiving member and directed across the direction in which said valve receiving bore opens into said receiving member, A motor receiving bore disposed outside of the two valve rows in the receiving member and directed perpendicular to the pump bore, Two low pressure accumulator bores which are opened into the receiving member outside of the two valve rows and open into the receiving member perpendicular to the axes of the valve receiving bore and the pump bore, Two hollow cylindrical noise damping chambers connected to said pump bore and hydraulically connected to two brake pressure generator ports opening into said receiving member, and A hydraulic assembly comprising several pressure fluid channels connected to the valve receiving bore, the pump bore and the low pressure accumulator bore and providing a hydraulic connection between the brake pressure generator port and the wheel brake port opening into the receiving member, The two noise damping chambers 6 are integrated with the pump bore 3, The brake pressure generator port THZ is hydraulically connected to the noise damping chamber 6 by a pressure fluid channel 3 ′ which opens radially or tangentially into the pump bore 3. The channel (3 ') is connected to the valve receiving bore (2) of the first valve row (X) for receiving the inlet valve. 2. The noise damping chamber (6) according to claim 1, wherein the noise damping chamber (6) is located at both ends of the pump bore (3), so that both the noise damping chamber (6) and the pump bore (3) are outside of the receiving member (1). Hydraulic assembly, characterized in that it is closed so as to be airtight with respect to the pressure fluid by a closing member (7) inserted in the two sides. A pump suction channel (5 ') is provided between the low pressure accumulator bore (5) and the pump bore (3), the channel (5') being perpendicular to the pump bore (3). A hydraulic assembly which is opened into the pump bore and is preferably produced by milling around the interior of the pump bore (3). 4. Hydraulic assembly according to any one of the preceding claims, characterized in that the pump bore (3) has an axial offset on both sides of the motor receiving bore (4). 2. An outlet valve according to claim 1, wherein the second valve train (Y) is arranged between the pump bore (3) and the first valve train (X) exclusively including the valve receiving bore (2) for the inlet valve. A hydraulic assembly comprising exclusively a valve receiving bore (2), said second valve row (Y) extending directly along the pump bore (3). 4. Hydraulic assembly according to claim 3, characterized in that a non-return valve which is deflected and closed in the direction of the low pressure accumulator bore (5) is mounted to the pump suction channel (5 '). 2. The vehicle according to claim 1, wherein any one or both of the wheel brake ports HR, HL, VL and VR and the brake pressure generator port THZ are at least partially arranged parallel to the motor receiving bore 4, the ports being A hydraulic assembly, characterized in that is opened into the receiving member (1) next to the motor housing projecting from the motor receiving bore at the top of the receiving member (1). 8. The valve control device according to claim 7, wherein the valve control device further comprises a control electronics for driving an electric motor for a radial piston pump integrated in the motor housing, the valve control device having a receiving member (1) opposite the motor housing. Mounted on the lower part of the hydraulic motor, wherein the electric plug of the electric motor projects through the through bore (8) disposed between the two valve rows (X, Y) and contacts the valve control device.