JPH0456887B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION Field of Industrial Application The present invention provides a flow regulating valve having a measuring throttle and a pressure balancing device in a housing, an attached throttle piston configured to be displaceable, and a pressure balancing piston receiving a spring load. controls the pressure gradient occurring at the measuring throttle to a constant value, a throttle piston and a pressure balancing piston are arranged coaxially with each other in the housing,
each having at least one control lip cooperating with a corresponding control lip on the housing;
This invention relates to a hydraulic flow regulating valve with a direct control structure.

BACKGROUND OF THE INVENTION Such a flow regulating valve is known from German Utility Model No. 1788185, in which the measuring throttle and the pressure equalization device are arranged coaxially with one another along with the displacement device. A manually displaceable flow control valve operates as a direct control valve controlling three ports. A disadvantage of this flow regulating valve is that the throttle piston is configured with a beveled edge and is rotatably guided in a sleeve that is fixed to the housing. The spool holes of the sleeve and the housing belonging to the pressure equalization device are formed in multiple stages, and intersecting tilt control holes are also required for pressure transmission. The housing is therefore relatively expensive to construct and is not suitable for various modifications. Another drawback is that no load can be applied to the residual flow connection port. In the initial position of the valve, the constant flow connection is also not closed. This valve is also not suitable for incorporating a check valve between the constant flow connection and the inlet connection.

Furthermore, the Federal Republic of Germany patent application publication no.
A 4-port, 3-position directional control valve with a vertical spool is also known from document 2423656, the housing of which has five side-by-side working chambers which are penetrated by spool holes. There are two motor chambers adjacent to a centrally arranged inlet chamber, and two return chambers adjacent to the outside of these motor chambers and connected to one another by a transverse passage. Such housings are produced in large quantities for directional control and are therefore inexpensive, and the control edges are machined with high precision in the housing lands between the individual working chambers. It is disadvantageous, however, that this housing is only used for directional control valves for directional control of the flow of pressure medium.

Furthermore, from FIG. 4 of the supplementary edition "Hydraulics and Pneumatics", Vol. 22, No. 3, published in March 1978, a proportional flow regulating valve is known which consists of a throttle valve and an intermediate plate with a pressure equalization device. The housing of a five-chamber directional control valve is used here for the throttle valve and is connected in a manner allowing flow in both directions of the pressure equalization device. A disadvantage of this flow regulating valve is that two separate housings are used for the throttle valve and the pressure equalization device, which makes the flow regulating valve relatively expensive and bulky.

Problem to be Solved by the Invention The problem to be solved by the present invention is to use the standard housing of a spool directional control valve, which is produced in large quantities and at low cost, as a common flow rate regulating valve housing, and to configure the housing with a measuring orifice and a pressure equalization device. The purpose of the present invention is to easily and inexpensively manufacture various flow rate regulating valves.

Means for Solving the Problem In order to solve this problem, according to the invention, a vertical spool valve structure with a spool hole receiving a throttle piston and a pressure balancing piston as a housing is provided.
A standard housing for port directional control valves is used, with five axially aligned working chambers separated from each other by four housing lands, the central inlet chamber being located between the two motor chambers. There is a return chamber on the outside of each of these motor chambers, which are connected to each other by a horizontal passage.
All five working chambers in the standard housing are each connected to a connection in the flange face, and at least two of the housing lands form housing fixed control edges corresponding to the control edges of the throttle piston and the control edges of the pressure equalization piston. ing.

Effects of the Invention Thus, according to the present invention, there are five operations consisting of one inlet chamber located in the longitudinal center of the spool hole, two motor chambers located on both sides of the inflow chamber, and return chambers located outside of both motor chambers. A four-port directional control valve having a chamber, a transverse passage connecting both return chambers to each other, a connection port in the flange surface communicating with these working chambers, and a housing land separating these working chambers from each other and forming a control edge. By using a standard housing and combining different configurations of throttle pistons and pressure equalization pistons, different flow regulating valve configurations in the form of 2-port and 3-port valves are possible. In a three-port configuration, the residual flow connection can be configured to be load-bearing or non-load-bearing. A safety function is also obtained in case of an emergency, since the flow regulating valve can be simply constructed with a measuring throttle which is closed by spring force in the non-actuated state.

Embodiments By means of the measures listed in the embodiment section of the patent claims, advantageous developments and improvements of the flow regulating valve are possible using the housing according to claim 1. In particular, according to claims 5 and 6, separate springs can be provided for the throttle piston and the pressure-equalizing piston, so that the measuring throttle can be operated with a stiffer spring according to different requirements;
Particularly advantageous. 3 according to claim 9
An advantageous configuration is obtained in the port flow regulating valve,
The residual flow connection can thereby be loaded. Claim 10 allows a particularly simple construction. The embodiment according to claim 11 is particularly advantageous, as it results in a flow regulating valve of simple and compact construction, which valve has three
It can be operated in two different ways, namely as a 2-port valve and the residual flow outlet unloaded or as a 3-port valve with a load. According to claim 13, an additional check valve function is combined in the two-port flow regulating valve. Further advantageous developments emerge from the further claims, the drawing and the description.

DESCRIPTION OF THE PREFERRED EMBODIMENTS FIG. 1 shows a first flow regulating valve 10 configured as a directly controlled three-port valve and producing a loadable residual flow. The valve essentially consists of a variable measuring throttle 11 and a pressure balancing device 12 connected downstream of the measuring throttle 11, both of which are arranged in a housing 13. A proportional electromagnet 14 is provided on the end face 16 of the housing 13 as a displacement device for the measuring diaphragm 11, and the opposite end face 17 of the housing 13 is closed with a lid 15.

As housing 13, a standard housing of a vertical spool directional control valve is used here, which has a through spool bore 18 between its end faces 16 and 17. The spool hole 18 is connected to the housing 13
It passes through five symmetrically arranged working chambers arranged in the axial direction on the inside and spring chambers 25, 26 on the outside, which open towards the end faces 16, 17. Of the five operating chambers, the central chamber serves as the inflow chamber 19;
The chambers next to it are the first motor chamber 21 and the second motor chamber 21.
serves as the motor chamber 22 of
It is useful as a. All operating chambers 19 to 24
is connected to an accessory connection port on the flange surface 27 of the housing 13. That is, the inflow chamber 19 is connected to the pump connection port 29 and the first motor chamber 2
1 is connected to the A connection port 29, and the second motor chamber 2
2 is connected to the B connection port 31 and is connected to the second return chamber 24
leads to the R connection 32, and a transverse passage 33 in the housing 13 connects the two return chambers 23, 24 to each other. The five operating chambers 19 to 24 are 4
They are separated from each other by two housing lands 34-37. These housing lands 3
4 to 37 are all machined on both sides in the area of the working chamber, thereby forming two precise control edges 38 fixed to the housing. Thus, in the housing 13, a total of eight control edges 38 are available for flow regulating valves of different constructions. The outer return chambers 23 and 24 are sealed lands 39 and 41, respectively.
These sealing lands 39, 41, unlike the housing lands 34-37, do not form a control edge. The housing 13 has both spring chambers 2
Chamber-like extensions 42 and 43 are formed upwardly from 5 and 26, and a transverse hole 44 formed from the end face 17 passes through these extensions 42 and 43. A sealing plug 45 inserted into this side hole 44 is connected to both extensions 4.
Pressure medium connection between 2 and 43 is prevented.

In the left-hand part of the spool bore 18 in the area between the first motor chamber 21 and the first spring chamber 25, a throttle piston is guided in a leak-tight manner as part of the measuring throttle 11. ing. The throttle piston 46 is connected to a return spring 47 provided in the spring chamber 25.
is pushed into the initial position shown, in which position its left end is supported by the housing of the electromagnet 14. At the initial position of the throttle valve 46, the proportional electromagnet 1
The push rod 48 of No. 4 is in contact. Throttle piston 46
has two piston parts 49 , 51 , the second piston part 51 of which is slidably guided in the first sealing land 41 so that the first return chamber 2
3 is separated from the spring chamber 25. The first piston part 49 is guided in the first housing land 34 and breaks the connection between the first motor chamber 21 and the first return chamber 23 in the illustrated initial position of the throttle piston 46 . A first control edge 52 is provided on the side of the first piston part 49 that is closer to the second piston part 51 and that controls the first housing land 34 .
It cooperates with the right-hand control edge 38 located at. A balance bore 53 in the throttle piston 45 transmits the pressure from the first motor chamber 21 to the spring chamber 25, which is sealed from the outside by the electromagnet 14, so that the pressure on the throttle piston 46 is balanced.

In the right side of the spool hole 18 in the range between the first motor chamber 21 and the second spring chamber 26,
As part of the pressure equalization device 12, a pressure equalization piston 54 is guided in a leak-tight manner. This pressure balancing piston 54 has an inner piston part 55 and an outer piston part 56. The outer piston part 56 is guided in the second sealing land 41 so that the second return chamber 24 is separated from the second spring chamber 26 . The second spring chamber 26, which is closed to the outside by the lid 15, has an adjustment spring 57.
This spring 57 is supported on the one hand by the lid 15 and on the other hand by the flange of the pressure equalizing piston 54. Under the force of the adjusting spring 57, a stop ring 58 attached to the pressure-balancing piston 54 rests against the second sealing land 41, thereby defining the initial position of the pressure-balancing piston 54. Since the stopper ring 58 is constructed as a U-shaped disc and is held in that position by a retaining ring 58',
The pressure-balancing piston 54 can be lathed and centerlessly ground with little machining effort. The inner piston part 55 is guided essentially in the area of the third housing land 36 . At the right end near the outer piston 56 the inner piston part 55 has a second control edge 59 .
cooperates with the left-hand control edge 38 on the fourth housing land 37. This second control edge 59, which provides a constant flow control, in the illustrated initial position of the pressure-balancing piston 54, is able to flow from the second return chamber 24 into the second
connection to the motor chamber 22. Furthermore, the inner piston part 55 has at its opposite end close to the throttle piston 55 a third control edge 61 which cooperates with a housing-fixed right control edge 38 in the second housing land 35. do. In the illustrated initial position of the pressure equalizing piston 54, the third
The control edge 61 is connected from the first motor chamber 21 to the inflow chamber 1
Connection to 9 is blocked. The third control edge 61 which carries out the control of the residual flow is therefore the second control edge 59
works in the opposite way. In the region of the outer piston part 56 the pressure-balancing piston 54 has a pressure passage 62;
This pressure passage 62 transmits the pressure of the second return chamber 24 to the second spring chamber 26 .

The operation of the flow regulating valve 10 will be explained below, with reference also to the circuit symbol according to FIG. As shown in FIG.
3 to which a directly controlled measurement aperture 11 is connected on the upstream side of the
Operates as a port valve. Pressure balance piston 54
is configured such that the residual flow exiting from the P connection port 28 can be loaded by the second control edge 59 and the third control edge 61. The incoming pressure medium stream is fed to the flow regulating valve 10 at the A connection 29 and a constant flow can be taken off at the B connection 31. The R connection 32 is not used and is closed in an arbitrary manner.

In the illustrated initial position of the throttle piston 46, the first control lip 52 interrupts the connection from the first motor chamber 21 to the first return chamber 25, so that the load connected to the B connection 31 is Hydraulically isolated. This also provides a safety function, since in the case of no current in the electromagnet 14 or an emergency cut-off, the return spring 47 pushes the throttle piston 46 into the initial position shown.

When the proportional electromagnet 14 is excited, this electromagnet 1
4 pushes the throttle piston 46 to the right with its push rod 48 against the force of the return spring 47.
A control edge 52 makes a connection from the first motor chamber 21 to the first return chamber 23 . Since the size of the flow cross section opened is proportional to the magnitude of the current value applied to the electromagnet 14, the flow cross section opened by the first control edge 52 can be arbitrarily set between zero and a maximum value. The pressure medium flowing via the first control edge 52 passes from the first return chamber 23 via the transverse channel 33 to the second
to the return chamber 24 of the pressure equalizing piston 5.
The B connection 31 is reached via the second control edge 59 located at 4. The pressure upstream of the first control edge 52 simultaneously acts on the left end face of the inner piston part 55 , the pressure downstream of the first control edge 52 reaches the second spring chamber 26 via the pressure channel 62 , A load is then applied to the pressure balancing piston 54. The pressure gradient occurring at the measuring throttle 11 therefore acts on the pressure balancing piston 54 against the force of the adjusting spring 57. In a known manner, a constant flow is thus created via the first control edge 52 and the second control edge 59 to the B connection 31 , and the third control edge 61 directs the residual flow to the P connection 28 . In this case, the throttle piston 4 is
6 is relieved of pressure, so that the electromagnet 14 essentially only has to overcome the force of the return spring 47.

The flow regulating valve 10 can be used for three use cases without any modifications. First of all, it can operate as a three-port flow regulating valve, the residual flow taken from its P connection 28 being supplied to the load and therefore able to carry the load. Second, the valve can be used as a three-port valve, with the P connection 28 being depressurized to the tank, so that the residual flow is not pressure loaded. Thirdly, this valve can be used as a two-port flow regulating valve with the P connection port 28 closed. Furthermore, a flow regulating valve 10 can also be used so that the pressure medium can freely return from the B connection 31 to the A connection 29. This takes place when the proportional electromagnet 14 receives the maximum current value, so that the first control edge 52 completely opens the connection path to which it belongs. Therefore, the flow rate regulating valve 10
can be used universally.

FIG. 3 shows a second flow regulating valve 70 which differs from the flow regulating valve 10 according to FIG. I am using it. The second flow regulating valve 70 has a different pressure-balancing piston 71, the inner piston part 55 of which is designed short and thus without the third control edge 61. Furthermore, in this flow regulating valve 70 the P connection 28 and the R connection 32 are closed in any manner and are therefore not used. This results in the third
As shown in the figure, a two-port flow regulating valve is created, and the first
The only difference from the flow regulating valve according to the figure is in the pressure balancing piston 71, which has changed slightly. Therefore, when the flow rate adjustment valve 10 is used as a two-port valve, the operation of the second flow rate adjustment valve 70 is the same as that of the first flow rate adjustment valve 10. Due to the absence of the third control edge 61, the second flow regulating valve 70 is constructed with correspondingly less outlay.

The third flow regulating valve 75 shown in FIG. 5 differs from the second flow regulating valve 70 shown in FIG. 3 in the following points, and the same parts are denoted by the same reference numerals.
As can be clearly seen from the circuit symbol according to FIG. 6, the third flow regulating valve 75 is provided with a check valve function, allowing unimpeded backflow from the B connection 31 to the A connection 29. For this purpose, the third flow regulating valve 75 has a different pressure-balancing piston 76, which piston 76 and the pressure-balancing piston 71 of FIG.
The only difference is that it is incorporated. The check valve 77 opens toward the first motor chamber 21 . The inner piston part 55 has an opening 78 in the area of the second motor chamber 22 through which a free return flow is possible. Note that the operation of the third flow rate adjustment valve 75 is the same as that of the second flow rate adjustment valve 70 in its flow rate adjustment function.

The fourth flow regulating valve 80 shown in FIG. 7 differs from the flow regulating valve 70 shown in FIG. 3 in the following points, and the same parts are designated by the same reference numerals. As can clearly be seen from the corresponding circuit diagram according to FIG. 8, the important difference is the connection after the measuring throttle 11, ie downstream of the pressure equalization device 12. In FIG. 7 this means that the proportional electromagnet 14 with its associated throttle piston 81 is now on the right end face 17.
attached to the lid 15 and the pressure balancing piston 8
2 is achieved by being installed from the other end face 16.

The throttle piston 81 has a second control piston 81 only in that its inner piston part 49 with the first control edge 52 is now designed wider and always interrupts the connection from the second motor chamber 22 to the inflow chamber 19. This differs from the throttle piston 46 according to FIG. The first control edge 52 on the throttle piston 81 now cooperates with the left control edge 18 on the fourth housing land 37 .

The pressure-balancing piston 82 is similar to the pressure-balancing piston 71 according to FIG. 3 only in the arrangement of the pressure channel 62.
, this pressure passage 62 now emerges from the annular groove between the two piston parts and passes through the inner piston part 55. In this way, the first return chamber 23
The pressure present in the inflow chamber 19 is passed through the pressure passage 62
transmitted to. From there, the same pressure can reach the right-hand spring chamber 26 via the balancing hole 53 in the throttle piston 81. Now pressure balanced piston 82
The second control 59 on the pressure-balancing piston 82 cooperates with the right-hand control edge 18 of the first housing land 34 due to its inverted installation.

As in the previous flow regulating valve, the first control lip 52 in its initial position closes off the associated pressure medium connection, and the second control lip 59 on the pressure balancing piston 82 opens it. The transverse hole 44 extending into the housing 13 now has an aperture 8 instead of a sealing plug 45.
3 and is connected to the second motor chamber 22 and the extension 42 via a radial hole 84 .

The action of this fourth flow regulating valve 80 largely corresponds to the action of the two-port flow regulating valve 70, but the measuring throttle 11 and the pressure equalization device 12 are arranged interchangeably. The pressure difference occurring across the measuring throttle 11 then again acts on the pressure balancing piston 82 against the force of the adjusting spring 47. In this case, the pressure upstream of the first control edge 52 on the throttle piston 81 reaches the first return chamber 23 via the transverse channel 33 and reaches the inflow chamber 19 via the pressure channel 62 on the pressure equalization piston 82 . The pressure downstream of the first control edge 52 passes from the second motor chamber 22 via a radial bore 84 and a transverse bore 44 with a throttle 83 to the left-hand spring chamber 25 and from there to the pressure-balancing piston 82.
Apply a load to. Therefore, the fourth flow rate regulating valve 8
0 controls constant flow to the B connection port 31.

FIG. 9 shows the fifth flow regulating valve 85 and the tenth flow regulating valve 85.
The figure shows the accompanying circuit symbols. This fifth flow rate regulating valve 85, like the second flow rate regulating valve as a two-port valve in FIG.
2 is constructed with a measuring diaphragm 11 connected after the latter, and differs from the latter in the following points, and the same parts are denoted by the same reference numerals.

The fifth flow regulating valve 85 has a different pressure balancing piston 86 and is held in its initial position by further stops 87, 88 on either side of the regulating spring 57. The second control edge 59 is now the outer piston part 5
6, and an opening for a pressure passage 62 is likewise formed here. Therefore the second control edge 59
cooperates with the right-hand housing fixed control lip 38 on the fourth housing land 37. The stop ring 87 is extended sleeve-like towards the stop ring 88 and forms a travel limit for the adjustment spring 57 which is now under tension when the second control edge 59 throttles or closes its associated connection path. .

The action of the fifth flow regulating valve 85 substantially corresponds to the action of the second flow regulating valve 70 according to FIG. 3, but in contrast to FIG. A pressure medium flows through it from the outside to the inside. In such a flow, the force of the flow acting on the pressure equalizing piston 86 is smaller than in the case of flow from the inside to the outside, so the fifth flow regulating valve 8
5 is not affected by vibration much.

FIG. 11 shows a sixth embodiment of a flow regulating valve 90, to which the circuit symbol according to FIG. 4 applies. This sixth flow regulating valve 90, like the second flow regulating valve 70 according to FIG. 3, is designed as a two-port valve and has a measuring throttle upstream of the pressure equalization device. The sixth flow rate regulating valve 90 is configured such that the control member is a hollow spool.
It differs from the flow regulating valve according to FIG. 3 by the advantage that only one spring is required.

The sixth flow regulating valve 90 has a throttle piston 91 configured as a hollow spool, the inner first piston part 92 of which is designed like a sleeve, and the outer first piston part 92 by means of a radial bore 93. The edge separated from the piston part 51 and located inside the radial bore 93 forms a first control edge 52, the inner piston part 92 closing the first motor chamber 21 in the initial position shown.

The sixth flow regulating valve 90 furthermore has a pressure-balancing piston 94 whose inner sleeve-like end forms a second control edge 59 by a cut-out recess 95 in the end face. This second control edge 59
cooperates with the right-hand control edge 38 on the third housing land 36. Pressure balance piston 94
An adjustment spring 96 is supported by the adjusting spring 96 and extends through the inflow chamber 19, and the other end is supported by the throttle piston 91. The pressure equalization piston 94 is therefore held in its initial position by the adjusting spring 96 and is supported on the lid 15 in this initial position.

A diaphragm 83 is provided in the side hole 44 of the housing 13. This lateral hole 44 emerges from the right-hand end face 17 and extends blindly through the housing 13 , and its end is connected to the first motor chamber 21 by a radial hole 97 .

The action of the sixth flow regulating valve 90 corresponds to a large extent to the action of the second flow regulating valve 70 according to FIG. After that, the constant flow passes through the sleeve-like part 92 and further through the inlet chamber 19 and through the second control lip 51 to the B connection 31 . The pressure downstream of the first control edge 52 acts in the same way through the spool bore 18 on the end face of the pressure balancing piston 94 which is loaded by an adjusting spring 96 . The pressure upstream of the first control edge 52 is conducted via the radial hole 97 and the transverse hole 44 into the right-hand spring chamber 26, so that the pressure balancing piston 94 moves against the force of the adjusting spring 96 against the first control edge. 92. The transverse passage 33 between the two return chambers 23, 24 thus serves no function. Sixth flow rate adjustment valve 90
This valve has the advantage of being low in cost, since it requires only one spring and has only a relatively short flow path. Because of this structure, in which the regulating pressure gradient varies as a function of the position of the measuring throttle, the sixth flow regulating valve 90 is advantageously used in the position regulating circuit.

FIG. 12 shows the seventh flow rate regulating valve 100, and FIG. 13 shows corresponding circuit symbols. This seventh flow regulating valve 100, like the fourth flow regulating valve 80 according to FIG. I have it too. However, unlike the fourth flow rate regulating valve shown in FIG. 7, it is configured to operate as a 3-port valve;
The residual flow arriving at the connection port 32 cannot be loaded.

For this purpose, the seventh flow regulating valve 100 has a throttle piston 101, of which the second piston part 51 on the outside is designed significantly wider than in FIG. room 2
4 and two adjacent housing lands 3
7, 41 so as to be slidable. In contrast to FIG. 7, the first control lip 52 on the inner piston portion 49 of the seventh flow regulating valve 100 cooperates with the left control lip 38 on the third housing land 36.

The seventh flow regulating valve 100 also has a different pressure balancing piston 102 compared to FIG. The end of this piston part, which is closer to the motor chamber 21, has a third control edge 61. This control edge 61 in the residual flow now cooperates with the left control edge 38 in the first housing land 34. Therefore, the connection from the first motor chamber 21 to the inlet chamber 19 is via the control members 101, 102.
It is not affected by either. Furthermore, the housing 13
is constructed as in the fourth flow regulating valve according to FIG.

The operation of the seventh flow rate regulating valve 100 will be explained below. As shown in FIG. 13, this valve operates as a 3-port flow regulating valve. The pressure medium flow arriving at the A connection 29 is split into a constant flow which is led via the inlet chamber 19 and the first control edge 52 to the B connection 31 . The pressure difference created on the first control edge 52 acts on the pressure balancing piston 102 against the force of the adjusting spring 57 . The third control edge 61 of the pressure balancing piston 102 therefore always controls the connection from the first motor chamber 21 to the first return chamber 23 so that the pressure gradient occurring at the measuring throttle 11 is controlled by the regulating spring 5.
7 and therefore remains constant. The residual flow controlled by the pressure-balancing piston 102 flows via the transverse channel 33 into the second return chamber 24 and can be taken off via the R connection 32 . 1st
The flow regulating valve 100 thus acts like a bypass flow regulating valve to the tank and the residual flow cannot be loaded. In other words, in order for the residual flow to be able to be loaded, not only should there be three connections, but also two control edges operating in opposite directions must be provided on the pressure-balancing piston. Therefore, the throttle piston and the pressure equalization piston must have a total of at least three control edges, whereas the pressure equalization piston 102 has only one control edge 61 in this case.

FIG. 14 shows an eighth flow regulating valve 105, which differs from the flow regulating valve according to FIG. 12 in the following points, and the same parts are designated by the same reference numerals.

The eighth flow regulating valve 105 acts on a further throttle piston 106, which is configured as a hollow spool in the same housing 13 as in FIG. This throttle piston 106 has annularly arranged control holes 107 in the region of its sleeve-like design, which are closed by the fourth housing land 37 in the illustrated initial position of the throttle piston 106 . These control holes 107 are connected to the first control edge 52
, whose control edges 52 cooperate with the left-hand control edge 38 of the fourth housing land 37 . In the initial position shown, the throttle piston 106
isolates the second motor chamber 22 and the second return chamber 24 from adjacent chambers.

The eighth flow regulating valve 105 has a different pressure-balancing piston 108, which pressure-balancing piston 108
is a pressure-balancing piston 102 according to FIG. 12 in that it has a second control edge 59 in constant flow on its inner first piston part 55.
It is different from Its outer piston part 56 has a third control lip 61 which serves for residual flow control. The second control edge 59 cooperates with the right control edge 38 on the second housing land 35 , and the third control edge 61 corresponds to the left control edge 38 on the first housing land 34 . Therefore, the control edge 59
and 61 operate in the opposite direction.

The action of the eighth flow regulating valve 105 largely corresponds to the action of the three-port flow regulating valve 100 according to FIG. Then, the residual flow arriving at the R connection port 32 is guided to the load,
Therefore, a load can be applied. A constant flow that separates in the first motor chamber 21 is connected to the spool hole 1.
8, passes through the second throttle 59 of the pressure-balancing piston 108 and reaches the B connection 31 via the control hole 107, which serves as the first control lip 52.

It is of course possible to modify the illustrated embodiment of the flow regulating valve without departing from the spirit of the invention, in particular by means of a suitable configuration of the control elements throttle piston and pressure equalization piston, and Different flow modes are also possible through a suitable configuration of the pressure-transmitting transverse holes 44. Therefore, the four connection ports A, B, P on the flange surface 27,
It is also possible to associate different flows with R.

Instead of a drive via a proportional electromagnet, other drives are also conceivable, for example mechanical displacements via a handwheel or rotary knob and screw shaft of the measuring diaphragm, or hydraulic or pneumatic displacements. Furthermore, displacement via an electromagnet whose position is adjusted with a displacement detector is also conceivable.

In flow regulating valves for larger flow rates, any type of detent may be provided for the throttle piston and the pressure equalizing piston to prevent flow fluctuations associated with different rotational positions of the pressure equalizing piston within the housing. . Providing the throttle piston and the pressure equalization piston directly in the housing without an additional sleeve results in a simple and inexpensive construction.

[Brief explanation of the drawing]

FIG. 1 is a vertical sectional view of a first embodiment of a flow rate regulating valve with a three-port structure in which residual flow can receive a load;
Fig. 2 is the circuit symbol diagram, Fig. 3 is a vertical cross-sectional view of the second embodiment of the 2-port structure, Fig. 4 is the circuit symbol diagram, and Fig. 5 is the 2-port structure combining the check valve function. FIG. 6 is a longitudinal sectional view of the third embodiment, FIG. 6 is its circuit symbol, FIG. 7 is a longitudinal sectional view of the fourth embodiment in which a measuring orifice is connected after the pressure equalization device, and FIG. 8 is its circuit symbol. Figure 9 is a longitudinal sectional view of the fifth embodiment of the flow rate regulating valve in which the pressure medium flows from the outside to the inside through the control edge, Figure 10 is its circuit symbol, and Figure 11 is a two-port structure. A vertical cross-sectional view of the sixth embodiment with one spring, FIG. 12 is a vertical cross-sectional view of the seventh embodiment of a flow rate regulating valve with a three-port structure in which the residual flow is not subjected to any load, and FIG. 13 is its circuit symbol diagram. , FIG. 14 is a sectional view of an eighth embodiment as a three-port valve in which the residual flow can receive a load. 10...Flow rate adjustment valve, 11...Measuring throttle, 12...Pressure balance device, 13...Housing, 14...Electromagnet,
19...Inflow chamber, 21, 22...Motor room, 23, 2
4... Return chamber, 27... Flange surface, 28, 29,
31, 32, A, B, P, R... Connection port, 33... Side passage, 34-37... Housing land, 38, 5
2, 59, 61...control edge.

Claims (1)

[Claims] 1. The flow rate regulating valve has a measuring orifice and a pressure equalization device in the housing, and an attached throttle piston is configured to be displaceable, and the pressure equalization piston receiving a spring load keeps the pressure gradient occurring at the measuring orifice constant. in which the throttle piston and the pressure equalizing piston are arranged coaxially with each other in the housing, each having at least one control lip cooperating with a corresponding control lip in the housing; as throttle piston 46;8
1; 91; 101; 106 and pressure balancing piston 5
4; 71; 76; 82; 102;
A standard housing 13 of a port directional control valve is used, having five axially aligned working chambers 19, 21, 22, 23, 24 separated from each other by four housing lands 34 to 37, of which A central inlet chamber 19 is located between the two motor chambers 21 and 22, and these motor chambers 2
Return chambers 23 and 24 are located on the outside of the chambers 1 and 22, respectively, and are connected to each other by a transverse passage 33.
2, 23, and 24 are all connected to connection ports A, B, P, and R on the flange surface 27, respectively, and at least two of the housing lands 34 to 37 are
Throttle piston 46; 81; 91; 101; 106
control edge 52 and pressure balancing piston 54; 7
1; 76; 82; 102; 108; 1; 76; 82; 102; 108; 2 The spool hole 18 in the standard housing 13 is widened at both ends 16 and 17 to form spring chambers 25 and 2.
6, and these spring chambers 25, 26 are adjacent to each other by sealing lands 39, 41, respectively.
It is characterized by being separated from 3, 24,
A flow rate regulating valve according to claim 1. 3. One of the two spring chambers 25, 26 is closed by the lid 15 and the other spring chamber 26 or 25 by the displacement device 14 in a leak-tight manner, The flow rate regulating valve according to claim 2. 4 Throttle piston 46; 81; 91; 101; 1
06, in addition to the piston part 49, 92 forming the first control edge 52, a second piston part guided in a sealing land 39, 41 between the return chamber 23, 24 and the spring chamber 25, 26. 5. Flow regulating valve according to claim 1, characterized in that the piston part 51 has a pressure balancing hole 53 inside it. 5 Return spring 47 provided in spring chambers 25 and 26
The throttle piston 46; 81; 91; 101;
106 is loaded in the direction of the initial position which interrupts the associated connection path and is operatively connected to the proportional electromagnet 14 by means of a push rod 48 in the spring chambers 25, 26. Flow rate regulating valve according to scope 4. 6 Pressure balance piston 54; 71; 76; 82;
102; 108 is provided in the spring chambers 26, 25 and is loaded by an adjustment spring 57 supported by the lid 15, so that the spring chambers 25, 26 and the return chamber 23,
In addition to the sealing lands 39, 41 between the housing lands 34, 37, the housing lands 34, 37 are penetrated.
Flow rate adjustment valve described in section. 7 2 ports (flow rate adjustment valve 70; 75; 80; 8
5; at least two control edges 5 forming 90;
2.59. The flow rate regulating valve according to claim 1, characterized in that it has a diameter of 2.59. 8 three control edges 52 to form a three-port flow regulating valve capable of receiving loads in the return passage;
59, 61, the flow rate regulating valve according to claim 1. 9. Claims characterized in that the pressure-balancing piston 54, 108 is formed with two oppositely operating control edges 59, 61, allowing the residual flow connection 32 to be loaded. Flow rate regulating valve according to item 1. 10 Restriction piston 46, 81, 101 and pressure balance piston 54; 71; 76; 82; 102; 1
2. The flow rate regulating valve according to claim 1, wherein 08 has a solid spool structure. 11 The throttle piston 46 is the pressure balancing piston 54
is connected upstream of the
attached to the first housing land 34 between the motor chamber 21 and the return chamber 23 adjacent thereto, a pressure balancing piston 54 passing through the three housing lands 35, 36, 37 and the sealing land 41; A second control edge 59 corresponding to the constant flow is attached to the fourth housing land 37 between the other return chamber 24 and the second motor chamber 22, and a third control edge corresponding to the residual flow The edge 61 is the first motor chamber 2
1 and the inlet chamber 19 , both control edges 59 , 61 of the pressure-balancing piston 54 cooperate with the second housing land 35 located between the inlet chamber 19 and the inlet chamber 19 .
at opposite ends of the
A flow rate regulating valve (Fig. 1) according to claim 10. 12 In order to cause the pressure difference occurring across the measuring orifice 11 to act on the pressure-balancing piston 82 , the spring chamber 25 associated with this pressure-balancing piston 82 has an extension 42 and a transverse hole 4 extending parallel to the spool bore 18 .
4 passes through this extension 42 and taps off the pressure present downstream of the measuring throttle 11 via a radial bore 84. Figures 12 and 14). 13. A check valve 77, 87 is provided in one of the components of the throttle piston or pressure equalization piston in the two-port flow regulating valve 75, 85 to ensure unimpeded backflow from the constant flow connection 31 to the inlet connection 29. 7. The flow rate regulating valve according to claim 7 (FIGS. 5 and 9). 14 Throttle piston 91 and pressure balance piston 94
and are constructed in a hollow spool structure and accommodate between them only one spring 96 acting as an adjustment spring, this spring 96 passing through the inlet chamber 19 . Flow rate regulating valve according to item 1 (FIG. 11). 15. The flow rate regulating valve according to claim 1, wherein displacement of the throttle valve is performed mechanically via a rotary knob or a screw shaft. 16 first control edge 52 and second control edge 59
2. Flow regulating valve according to claim 1, characterized in that the pressure medium flows from the outside to the inside through each of the valves.