Regulating valve with switchable control edge

Abstract

The invention relates to a control valve having a switchable control edge, comprising a valve body (1) having a first control spool (400) and at least two control ports (501, 502, 503, 504, 505) and at least one control edge (6, 44, 45), the first control spool (400) having an axial bore (40) and a second control spool (41) being designed in the axial bore (40), and further comprising an end cap (57) having an actuating piston (48), where the actuating piston (48) is designed to engage into the axial bore (40) and the actuating piston (48) is designed to displace the second control spool (41) in the axial bore (40).

Description

[0001] The subject of the present invention is to integrate into an existing regulating valve a control mechanism which on the one hand enables a small relative overlap between the control edges P-A and A-T of the regulating valve in the regulating operation and on the other hand separates the A port from the T port in the rest state (in the case of a failsafe situation).

[0002] In the application of a hydraulic pilot 4 / 3-way regulating valve in a piston longitudinal spool embodiment (structure type plate structure valve) it is necessary to prevent in the rest state (in the case of a failsafe situation) a movement of the shaft of a plastic injection molding machine, for example of the injection unit, which is controlled or regulated by the regulating valve. Critical here is in particular the extension movement of the injection cylinder, which must be avoided.

[0003] This is usually achieved in that the P-control edge for coupling the pressure supply in the case of a failsafe situation overlaps sufficiently in order to prevent or at least minimize the fluid volume flow to the consumer.

[0004] Now, in order to prevent a retraction movement of the injection cylinder, the A-T control edge of the consumer, for example of the injection unit, must also be extended in an overlapping manner in order to prevent a fluid volume flow to the reservoir. Thereby an external force acting on the shaft, which would cause an unintentional movement of the shaft, can be prevented. Here, the valve in the form of a spool structure always has a clearance leakage due to the principle.

[0005] The failsafe situation represents a safe machine state in which the regulating valve is not in active electronic regulation - usually switched without current and voltage - and the control spool is not in active position regulation. In the failsafe situation the control spool is brought to an end position or a defined position by a mechanical failsafe mechanism (for example spring and / or end stop) and a switching valve.

[0006] On the other hand, in the (regulating) operation a small overlap of the P-A control edge and the A-T control edge of the regulating valve is necessary in order to be able to perform a precise shaft position regulation / pressure or force regulation.

[0007] The problem is that these two requirements contradict each other. The control spool is either manufactured with small overlaps or even with zero intersection of the control edges P-A and A-T, which enables a precise regulation, but in the case of a failsafe situation leads to a retraction drift movement of the shaft of the injection molding machine (because the A-T control edge already has an underlap), or the control spool is manufactured with overlapping control edges (for example P-A control edge and A-T control edge), which leads to an imprecise regulation, but for this purpose ensures a rest or a small movement of the shaft in the rest state (in the case of a failsafe situation).

[0008] It is known that the control slide valves are overlapped, which are electronically compensated when actively regulated, so-called dead band compensation, which however dynamically reaches its limits. Ultimately, in order to regulate the pressure or volume flow in the working port, a physical overlap of the control edges must always be passed, which can lead to a loss of the regulation result depending on the size of the overlap on the control slide valve (dead band to be passed) and the dynamic properties of the pilot valve, since a certain time is required to pass the area where the overlap occurs.

[0009] It is furthermore known that safety valves (usually seat valves) are connected in series to the regulating valve in order to decouple the consumer port or the pressure supply from the regulating valve. The seat valves additionally connected in series consume structural space. Correspondingly, the seat valves connected in series must be dimensioned to be large, since they must be adapted to the maximum volume flow of the regulating valve. Usually, their nominal size is also chosen to be larger in order to keep the pressure loss and thus the energy loss low when operating. The disadvantage is that depending on the switching dynamics of the regulating valve, the sealing of the seat valve can be subjected to severe stress, which makes the maintenance costs and maintenance times high. Furthermore, the additional seat valve is another cost factor.

[0010] Another known solution is to use separate regulating valves to control / regulate the two ports of the actuator independently of one another. Correspondingly, an independent fail-safe position can be set for each of these separate regulating valves (as required by the application), the disadvantage of this solution being that two or more regulating valves are required, which makes this solution expensive. Furthermore, the handling in terms of regulation is more complex.

[0011] Starting from the known prior art, it is the object of the present invention to provide a regulating valve with control edges which at least partially overcomes the disadvantages present in the prior art.

[0012] In particular, it is the object to integrate a handling mechanism into the existing regulating valve which on the one hand enables a small relative overlap between the control edges P-A and A-T in the (regulating) operation, thus enabling precise regulation, and on the other hand, in the rest state (fail-safe case, in which the A port has been separated from the pressure supply P by the overlapping P-A edge), additionally separates the A port from the T port, i.e. has sufficient overlap, thus ensuring that the shaft is at rest or has a sufficiently small shaft movement.

[0013] This object is achieved by the subject matter of the independent claims. Advantageous embodiments of the invention are described in the dependent claims and in the following description.

[0014] A regulating valve with switchable control edges can comprise a valve body and an end cap with an actuating piston. The valve body can be designed with a first control spool and at least one first and second control port and at least one control edge. Here, the first control spool can have an axial bore and in the axial bore can be designed with a second control spool.

[0015] The regulating valve can be a valve, in particular a hydraulic valve, which influences a pressurized liquid by means of flow path, direction and amount of volume flow or liquid pressure. According to the present disclosure, the regulating valve is a reversing valve with the structure and design of the effective surfaces (sealing surfaces) of the control spools, with the longitudinal valve with the effective movement.

[0016] The control edges can be movable edges in the valve, which regulate the flow of liquid or gas between the ports on the valve. The control edges are actuated by a force, for example a lever or an electric and / or pneumatic drive, and act by opening or closing the flow channel between two control ports in the valve body. In particular, the movable edges are surfaces of the first control spool and / or the second control spool, which can cover the openings of the flow channel of one and / or multiple control ports of the valve body and thereby partially or completely release and / or block the passage or flow path between the control ports. According to the invention, the valve body and the control spools form control edges that coordinate with each other, which can be displaced coaxially to each other, so that a flow path and / or a throttling takes place with the relative arrangement of the respective openings of the control ports in the valve body. The regulating valve according to the present disclosure can comprise at least three control edges.

[0017] The first control edge can be a control edge in the form of a piston-longitudinal spool structure known from a 4 / 3-way valve hydraulically piloted, which regulates the flow between the control ports A and T. The first control edge can be a first A-T control edge, which can also be referred to as an A-T1 control edge.

[0018] According to the present disclosure, the second control edge can be a new type of control edge, which, in addition to the first control edge, also regulates the flow between the control ports A and T. The second control edge can be a second A-T control edge, which can also be referred to as an A-T2 control edge.

[0019] According to the invention, the third control edge corresponds to the first control edge and can be manipulated by the axial displacement of the first control spool in such a way that the third control edge partially or completely releases the passage between the control ports P and A and / or correspondingly partially to completely closes it. The flow between these two control ports P and A can thereby be controlled and regulated. The third control edge can also be referred to as a P-A control edge.

[0020] The fourth control edge can be a control edge that regulates the flow between the control ports P and B. The fourth control edge can be referred to as a P-B control edge.

[0021] The fifth control edge can be a control edge regulating the flow between the control ports B and T. The fifth control edge can be referred to as the B-T control edge.

[0022] The control edges can be switchable. The switchable control edges can release and / or block the flow paths between the control ports in the valve body by actuating and adjusting the first control spool and / or the second control spool. According to the present disclosure, this can be done by an electric drive, a pneumatic drive, or a hydraulic drive, and / or a piezoelectric drive, or a magnetostrictive drive. The switchable control edges can enable a fast reaction to changes in the system and a precise control of the flow of liquid or gas in such a way that the control edges can be precisely switched from one position to another and enable a zero intersection between the regulating edges P-A and A-T in the activated position.

[0023] The control ports of the regulating valve according to the present disclosure can be ports in the valve body. The control ports can open into an annular channel in the valve body. For example, the line of the pressure supply source X of the pilot valve, and / or the return port Y to the tank, and / or the pressure supply source P of the valve body, and / or the further return port T to the tank, and / or the at least one working port A, B can be coupled to the control ports.

[0024] The first control port can be a T-control port. The second control port can be an A-control port. The third control port can be a P-control port. The fourth control port can be a B-control port. The T-annular channel on the B-side can be the space on the longitudinal section of the valve body that connects the first control port from the right side of the B-control port via a channel, in particular a tank bridge. This channel can be the T-channel on the B-side.

[0025] The first control spool and the second control spool according to the present disclosure can be hydraulic control spools. The control spools can be used in a spool-type directional valve. According to the present disclosure, the second control spool can be designed within the first control spool. The actuation directions of the two control spools are coaxial along their longitudinal axes, so that the respective control edges of the control spools completely, partially and / or not at all cover the openings of the control ports in the valve body depending on the position of the control spool that is displaced.

[0026] The first and second control spool can each comprise at least two piston lobes to the piston shaft, which form a control edge on the control spool. The first control spool can form a first and a second piston lobe. Furthermore, the first control spool can form a third piston lobe. In addition, the first control spool can form a fourth piston lobe. The second control spool likewise can form a first and a second piston lobe. Depending on the position of the first and / or second control spool, the piston lobes can cover control port openings in the valve body and thereby regulate the flow between the control ports. The piston lobes of the control spools can be arranged in the port area of the control ports. The piston lobes of the control spools, which cover the control port openings depending on the adjustment, can together with the openings of the valve body constitute the control edge.

[0027] The axial bore is a bore in the valve body and the first control spool along the longitudinal axis of the first control spool, so that the first control spool is displaceably received in the bore of the valve body and the second control spool is displaceably received in the bore of the first control spool. The bore can be centrally centered in the control spool.

[0028] According to the present disclosure, the regulating valve with switchable control edge can also have an end cap with an actuating piston. In this case, the actuating piston can be designed so that it engages into the axial bore and furthermore so that it displaces the second control spool in the axial bore of the first control spool.

[0029] The second control edge between the control ports T and A can thereby be manipulated. The second control edge can combine the functions of two valves for the disclosed regulating valve. On the one hand, in the case of activation of the failsafe valve, a zero intersection behavior can be ensured and thereby a good adjustability of the shaft coupled to the valve; on the other hand, in the case of deactivation of the failsafe valve, the leakage can be reduced to a minimum value that can correspond to a gap leakage. A second (seat) valve connected in series downstream can become superfluous. This can achieve cost, service / maintenance and structural space savings. Furthermore, this component does not need to be kept in stock as a replacement part. According to the present disclosure, the second (seat) valve, which is otherwise commonly connected in series (downstream), which can cause a pressure loss (increase), can be omitted. The regulating valve system with the regulating valve according to the present disclosure can be more energy-efficient than the combination of a regulating valve and a (seat) valve connected in series known from the prior art.

[0030] A connecting element can be designed between the actuating piston and the second control spool. Thereby axial and angular deviations can be compensated.

[0031] The connecting element can comprise a balance bar and at least two lock nuts. The first lock nut can abut against the second control spool. The second lock nut can abut against the actuating piston. The second lock nut can be designed as a mechanical stop and be case-hardened. The connecting element between the actuating piston and the second control spool can implement a coupling function and thus be a coupling element.

[0032] Thereby, axial deviations of the actuating piston and the second control spool running in the first control spool, which are caused by production, can be compensated.

[0033] Furthermore, the valve body of the regulating valve and the first control spool can form a first control edge (A-T1) and a second control edge (A-T2). Here, a smaller relative overlap between the second control edge (A-T2) and the third control edge (P-A) can be formed 。 The first control edge (A-T1) can have a sufficient overlap.

[0034] The second control spool can also be designed such that it independently of the first control spool manipulates the second control edge (A-T2), i.e. opens or closes. Thus, according to the present disclosure, a precise manipulation mechanism can be integrated into the regulating valve by means of the second control edge (A-T2). At the same time, in the rest state (fail-safe case), a flow path from one control port to the next control port can be prevented in such a way that the first control edge (A-T1) is overlapped sufficiently and thus a drifting movement of the retraction of a shaft, for example of an injection molding machine, is prevented.

[0035] Between the at least two control ports, a flow path can be formed and influenced by the control edges, so that the flow can be regulated.

[0036] According to the present disclosure, the overlap can be a positive overlap, a zero overlap or a negative overlap. A positive overlap can describe a control edge position of the piston nose of the first control spool and / or of the second control spool, which is longer than the width of the opening of the annular channel of the control port in the housing of the valve body.

[0037] The overlap refers to the total stroke of the first control spool or of the second control spool in the intermediate position or in the end position and can be given in percent [%].

[0038] A zero overlap (zero intersection) can be characterized by an aligned position of the control edges of the piston nose of the respective two control spools and by an aligned position of the annular channels of the control ports in the valve body housing. A zero overlap of the control edges can achieve a very short manipulation time or reaction time on the actuator coupled to the regulating valve, since the opening cross section of the annular channel of the respective control port in the valve body is released without delay and only a small manipulation displacement is required for the manipulation and regulation.

[0039] Negative overlap can describe the length of the control land of the piston nose of the respective control spool, which is smaller than the width of the annular channel of the control port in the housing of the valve body. Negative overlap can be underlap.

[0040] There can be a small overlap when the overlap of the respective control land is between 0% and 5%. A small overlap of 0% can be zero intersection.

[0041] Relative overlap can be the ratio between two overlaps. For example, the overlap of one control land and the overlap of another control land make up a sum. This sum can result in a relative overlap.

[0042] Relative overlap can be a small relative overlap when the sum is between 0% and 10%. The second control land (A-T2) can make up such a small relative overlap with the third control land (P-A).

[0043] A large overlap of the respective control land can be 10% or more. A sufficient overlap and / or a sufficiently large overlap can be between 10% and 20%. The first control land (A-T1) can have such a large overlap and / or a sufficient overlap. The third control land (P-A) can also have a large overlap. The large and / or sufficiently large overlap ensures that the shaft / actuator (e.g. injection unit) is shut down or its movement is sufficiently small in the case of a failsafe. The P-A control land (third control land) can have a large overlap.

[0044] According to the invention, the negative overlap and / or the underlap of the respective control land is less than 0%. The fifth control land (B-T control land) can have such an underlap.

[0045] The second control land (A-T2 control land) can have a groove-like annular channel. The groove-like annular channel can be machined into the piston nose. Alternatively and / or additionally, the second control land can have one or more control windows distributed in the circumferential direction.

[0046] The groove-like annular channel and / or the control window are formed at the input end and the output end, respectively, of the transverse bore of the first control spool. Both can have different shapes. Thus, the groove-like annular channel can have a rectangular cross-section, for example, or a cross-section with rounded corners at the base. In the case of the control window, the control window can likewise have different cross-sectional shapes, for example rectangular, triangular, circular or T-shaped.

[0047] The annular channel or control window can be specifically adapted in terms of manufacture to the third control edge (A-T2), in particular to the third control edge (P-A), in the valve body in axial direction. Thereby, the second control edge (A-T2) can enable a precise adjustment. Furthermore, in case of a fail-safe, the second control edge (A-T2) according to the present disclosure can separate the control port A from the control port T, since the second control edge (switchable by the inner second control spool) and the first control edge (A-T1) can be positioned together such that, when viewed from the outside, a sufficient overlap can be achieved at the first (A-T1), second (A-T2) and third (P-A) to ensure shaft standstill or sufficiently small shaft movement.

[0048] The annular groove or control window of the second control edge (A-T2) can be connected with the axial bore in the first control spool via at least one first lateral bore.

[0049] The first lateral bore can be formed in a first piston lobe of a plurality of piston lobes of the first control spool. The first piston lobe can have a plurality of first lateral bores. The first lateral bore can be perpendicular to the longitudinal axis of the axial bore of the first control spool. In a longitudinal section of the valve body of the regulating valve, the first piston lobe of the first control spool is formed at the leftmost side. The second control edge (A-T2) can be arranged in the first piston lobe.

[0050] The first lateral bore can constitute the second control edge (A-T2) in the first piston lobe. Thus, the first lateral bore can make the disclosed regulating valve combine the functionality of two valves. On the one hand, in the case of activation of the fail-safe valve, a zero-intersection behavior can be ensured and thereby a good adjustability of the shaft coupled to the valve; on the other hand, in the case of deactivation of the fail-safe valve, the leakage can be reduced to a minimum value which can correspond to a gap leakage. A second (seat) valve connected in series downstream can become superfluous. This can enable cost, service / maintenance and installation space savings. Furthermore, this component does not need to be kept in stock as a replacement part. According to the present disclosure, a second (seat) valve which is otherwise commonly connected in series (downstream) and can cause a pressure loss or an increase in pressure loss can be omitted. A regulating valve system with a regulating valve according to the present disclosure can be more energy-efficient than a combination consisting of a regulating valve and a (seat) valve connected in series known from the prior art.

[0051] The first control spool can form at least one second lateral bore in the port area of the second control port (A) of the valve body. Furthermore, the at least one second lateral bore can be connected with the axial bore of the first control spool.

[0052] The port area can be the part of the valve body that can be flowed into / flowed out by liquid or gas. The port area can be formed on the outside of the valve body and have a defined port diameter in order to be able to be fixedly connected with a control block, a pipe, a container or other system components. The port can have different shapes, including threaded, flanged or plug-in ports. The port area can be designed such that it extends into the valve body.

[0053] This can connect a second control edge (A-T2) in the first piston nose of the first control spool via an axial bore with a second lateral bore. The second lateral bore can form a flow inlet in the second piston nose of the first control spool, but alternatively also an additional control edge to the second control spool, which is part of the inner system of the first control spool. This alternative additional control edge can functionally adjust the flow between the control ports A and T via the second control edge (A-T2).

[0054] According to the present disclosure, the actuation piston can be designed to control the flow path via the second control edge (A-T2) by means of the second control spool.

[0055] The expression "via the second control edge" can mean that the flow path from one control port to the other control port is released. For this purpose, the axial displacement of the first control spool and / or the second control spool can release the flow path between the two control ports and thus regulate the flow.

[0056] This can enable precise regulation of the disclosed regulating valve, since a small relative overlap between the second control edge (A-T2) and the third control edge (P-A) is achieved during the regulating operation. In the case of a failsafe, the control port A can be separated from the control port T in such a way that the first control edge (A-T) and the third control edge (P-A) achieve a sufficiently large overlap and thus can ensure axial standstill or a sufficiently small axial movement.

[0057] For hydraulic compensation, the second control spool can have two surfaces with equally sized effective surfaces.

[0058] The surfaces can be designed annular or circular. The surfaces can be formed at the piston nose of the second control spool, respectively.

[0059] Thus, a load pressure applied to the second control port (A) does not lead to unintentional actuation of the second control spool. This in turn can enable precise regulation of the regulating valve according to the present disclosure. In the case of a failsafe, the second control port (A) can be separated from the first control port (T) in such a way that the first control edge (A-T1) and the second control edge (P-A) achieve a sufficiently large overlap and thus can ensure axial standstill or a sufficiently small axial movement in the case of a failsafe.

[0060] According to the present disclosure, the axial bore of the first control spool can comprise a chamber with an internal compression spring.

[0061] In a longitudinal section of the valve body, the chamber can be formed in an extension of the right end of the axial bore. The rear portion of the axial bore can comprise the chamber. The chamber can be seated in the first control spool at a height between the second piston nose and the third piston nose of the first control spool. The chamber can be formed at the height of the third port (P).

[0062] This can serve to receive a spring and to form a stop for the second control spool at the end position of the first control spool and / or the second control spool. This can enable precise adjustment of the regulating valve of the present disclosure. In a fail-safe situation, the control port A can be separated from the control port T in such a way that the first control edge (A-T1) and the second control edge (P-A) overlap sufficiently and thus can ensure that the shaft is at rest or has a sufficiently small shaft movement.

[0063] According to the present disclosure, an axial pressure relief bore can be designed coaxially to the axial bore. Here, the first control spool can have at least one third lateral bore in the region of the T-channel on the B-side, which is connected to the axial pressure relief bore. The T-channel on the B-side and the third lateral bore can constitute a leakage flow path.

[0064] The third lateral bore according to the present disclosure can be perpendicular to the axial pressure relief bore. The third lateral bore can discharge leakage from the inner system (chamber of the axial bore of the first control spool).

[0065] This can enable precise adjustment and handling of the regulating valve and, in addition, can prevent flow from one control port (A) to the next control port (T) in a rest state (fail-safe situation) in such a way that the first control edge (A-T1) overlaps sufficiently. This can, together with the third control edge (P-A) which overlaps in a fail-safe situation, ensure that the shaft is at rest or has a sufficiently small shaft movement.

[0066] It can be proposed that the second control spool forms a slot on its right-side end face. The slot can discharge leakage.

[0067] The right-side end face can be formed in the second end region of the second control spool. The left-side end face of the second control spool can be formed in the first end region of the second control spool. The left-side end face and the right-side end face can be formed at opposite end regions of the second control spool.

[0068] The slot can enable in the blocked state that a leakage from the chamber can be guided out of the axial bore. In this way it is prevented that due to the leakage volume flow pressure can accumulate in the chamber of the first control spool and the pressure opens the second control spool unintentionally. Thus, the disclosed regulating valve can enable a precise actuation mechanism and in a fail-safe situation separates the second control port (A) from the first control port (T). In this case the leakage can be guided out via the slot and nevertheless the shaft standstill can be ensured.

[0069] The end cap can comprise a valve and a spring chamber. The spring chamber can comprise a compression spring and a stopper.

[0070] In a longitudinal section of the valve body, the spring chamber and the end cap can be arranged at the first end of the valve body on the left side. Depending on the application, the end cap and the spring chamber can also be arranged on the right side of the valve body of the disclosed regulating valve.

[0071] The end cap can enable a precise actuation mechanism in the disclosed regulating valve by means of the actuating piston. In a fail-safe situation, the second control port (A) can be separated from the first control port (T) by precise regulation in such a way that the first control edge (A-T1) and the third control edge (P-A) form a sufficient overlap to ensure a shaft standstill or a sufficiently small shaft movement.

[0072] The spring chamber of the present disclosure can be connected with the valve body via a pressure relief bore.

[0073] The pressure relief bore can extend from the spring chamber and can end at the valve body, the pressure relief bore can continue to extend in the valve body. Thereby, a complete passage can be constituted and a flow path via the T-control port towards the tank direction can be enabled.

[0074] Thus, the spring chamber can constantly relieve pressure in the direction towards the tank and can ensure a precise control of the regulating valve.

[0075] The regulating valve of the present disclosure can be used as an injection regulating valve for controlling an injection unit of an injection molding machine.

[0076] In a regulating operation, a precise control of the injection molding machine can be enabled and in a fail-safe situation, a safe machine state of the injection molding machine, in particular a shaft standstill, can be enabled.

[0077] The regulating valve system can comprise a pilot valve, one or two fail-safe valves, and the regulating valve of the present disclosure. The fail-safe valve can be a safety valve.

[0078] The advantage is that in the adjustment operation a small relative overlap between the second control edge (A-T2) and the third control edge (P-A) can be achieved, which enables precise control and on the other hand in the case of a failsafe situation separates the A-port from the T-port, i.e. the first control edge (A-T1) and the third control edge (P-A) have a sufficient overlap and thus in the case of a failsafe situation a safe machine state of the adjustment valve system can be achieved.

[0079] In the case of an activated failsafe valve, the adjustment valve system can ensure precise adjustability of the shaft of the injection molding machine. In the case of a deactivated failsafe valve, the adjustment valve system can reduce the leakage to a minimum value which can correspond to a gap leakage and ensure in the case of a failsafe situation that the shaft is stationary or has a sufficiently small shaft movement. The adjustment valve system with the adjustment valve according to the present disclosure can be more energy-efficient than adjustment valves known from the prior art.

[0080] The design solutions and refinements described above can be combined with one another arbitrarily in a meaningful manner. Further possible design solutions, refinements and implementation forms of the present disclosure also include combinations of features described previously or subsequently with reference to the embodiments of the present disclosure which are not explicitly mentioned. Here, the skilled person can also add individual aspects as refinements or supplements to the respective basic form of the present disclosure, in particular.

[0081] The present disclosure is explained in detail below with the help of embodiments which are given in the schematic illustrations of the drawings. In the drawings: Figure 1 Fig. 1 shows an adjustment valve of the prior art, Figure 2 Fig. 2 shows an application example from the prior art, Figure 3 Fig. 3 shows a volume flow-signal function of the adjustment valve from the prior art, Figure 4 Fig. 4 shows a schematic diagram of the adjustment valve in an adjustment operation with zero intersection in the prior art, Figure 5 Fig. 5 shows a schematic diagram of the adjustment valve in a failsafe position with overlap and underlap in the prior art, Figure 6 Fig. 6 shows a schematic diagram of the adjustment valve according to the present disclosure in an adjustment operation with the second control spool open, Figure 7 Fig. 7 shows a schematic diagram of the adjustment valve according to the present disclosure in a failsafe position with the second control spool closed, Figure 8 Fig. 8 shows a volume flow-signal function of the adjustment valve according to the present disclosure, Figure 9 Fig. 9 shows a schematic diagram of the adjustment valve according to the present disclosure in a failsafe position with the second control spool closed, Figure 10 schematic view of a regulating valve according to the present disclosure in a regulating process, Figure 11 schematic view of a regulating valve according to the present disclosure in a regulated negative end position, Figure 12 schematic view of a regulating valve according to the present disclosure in a regulated positive end position, Figure 13 schematic view of an alternative regulating valve according to the present disclosure in a regulated negative end position, Figure 14 partial view of a schematic view of a left end cap of a regulating valve according to the present disclosure from Figure 17 Figure 15 further schematic view of a regulating valve in a fail-safe situation, Figure 16 schematic view of a regulating valve system according to the present disclosure in a fail-safe position with a second control spool closed, with valve electronics and a displacement measuring system, Figure 17 schematic view of a regulating valve system according to the present disclosure in a regulating process, with valve electronics and a displacement measuring system, Figure 18 schematic view of a regulating valve system according to the present disclosure in a regulated positive end position, with valve electronics and a displacement measuring system, Figure 19 schematic view of a regulating valve system according to the present disclosure, with valve electronics and a displacement measuring system.

[0082] The accompanying drawings are intended to facilitate a further understanding of embodiments of the present application. They illustrate embodiments and together with the description below are used to explain the principles and concepts of the present application. Numerous other embodiments and many of the noted advantages come to mind in connection with the illustrated embodiments as described and as claimed. The elements in the figures are not necessarily to scale, as emphasis is placed upon illustrating the principles and concepts of the present application.

[0083] In the drawings, identical, similar, and like elements in the figures are denoted with the same reference numerals, where possible. Where different elements are referred to with different, identical, similar, and like reference numerals where possible, it is intended that these elements differ in some way, as will be understood by those skilled in the art. Figures 6 to 14 In particular, embodiments build on one another, and thus for the sake of clarity, elements, features, and components that function in the same way (unless otherwise specified) are not all provided with reference numerals. However, the skilled person recognizes that they are elements, features, and components that function in the same way and that the corresponding reference numerals from previous figures can be supplemented.

[0084] ​It should finally be pointed out that the description and the embodiments of the application are not to be understood as being limiting in principle in respect of specific physical implementation of the application. All features described and illustrated in connection with the various embodiments of the application can be provided in different combinations in the subject matter of the application in order to achieve their advantageous effects at the same time.

[0085] The scope of the protection is given by the claims, without limitation to the features recited in the specification and / or shown in the drawings.

[0086] Figure 1 A schematic structure of a known prior art pilot 4 / 3 regulating valve is shown. The regulating valve consists of a valve body 1 (also called main stage), an optional fail-safe valve 2 (also called safety valve) and a pilot valve 3. In the valve body 1 a movable control spool 4 is accommodated. Figure 1 The control spool 4 in the valve body 1 forms four piston lobes. A first piston lobe 31, a second piston lobe 32, a third piston lobe 33 and a fourth piston lobe 34. Figure 1 The valve body 1 and the piston lobes 31, 32, 33, 34 of the control spool 4 in the valve body 1 have coordinated control edges to each other, for example control edges 5 and 6 between the control ports T and A. Here, the valve body 1 forms the fixed control edge 5 and the second piston lobe 32 of the control spool 4 forms the movable control edge 6, since the control spool is arranged displaceably in the valve body 1. Depending on the position of the control spool 4 within the valve body 1, the second piston lobe 32 releases the flow paths between the control ports T and A and between A and P.

[0087] In the event of a fail-safe valve 2 cut-out, the control spool 4 is pressed by a compression spring 7 and a mechanical stop (in the Figure 1 exhibited in the control chambers 12, 13 by the adjustable disc 8) to a predefined intermediate position and closes the corresponding control ports 9 (T, A, P, B) of the valve body 1 with the piston attachments 31-34.

[0088] The valve body 1 has the following control ports 9: • X - pressure supply of the pilot valve 3 and is preferably • Y - return port or tank port of the pilot valve 3, likewise preferably • P - pressure supply of the valve body 1 • T - return port or tank port of the valve body 1 • A and B - working ports, at which the injection cylinder 16 of the injection unit 15 of a consumer, for example an injection molding machine, is connected.

[0089] On the left side of the valve body 1, an end cap is arranged, which has electronics for controlling the control chambers 12 and 13. The end cap comprises a displacement measuring system 10 and a valve electronics 11. The position of the control slide 4 is measured by means of the displacement measuring system 10 and is adjusted by the valve electronics 11.

[0090] Via the pilot valve 3, the left control chamber 12 and the right control chamber 13 of the valve body 1 are applied with a volume flow and a pressure. Depending on the electrical actuation of the pilot valve 3, the control slide 4 is deflected from the middle position to the left or to the right and thus releases the corresponding flow paths P-A and B-T or P-B and A-T.

[0091] Figure 2 A schematic diagram of an injection unit 15 with a regulating valve, which is an injection regulating valve 14, is shown. In this application example of the invention, the regulating valve 14 controls the injection unit 15 of an injection molding machine. When the protective grid of the machine is opened, a failsafe situation occurs and the regulating valve must be brought into a safe state. In any case, the injection cylinder 16 must not move the injection unit 15 forward and thus extend it. This means that the working port of the regulating valve, which is connected to the cylinder chamber / cylinder surface 17 of the injection cylinder 16, which enables the injection movement, must not be applied with pressure in any case.

[0092] When plastic melt is plasticized or in turn in the configuration operation, an external force is applied by the plastic melt in the injection cylinder, which places the injection cylinder in a movement opposite to the injection movement. In certain applications or in particular in the configuration operation when the protective door is opened, this movement is not desired for process-technical reasons. In order to prevent this movement, the volume flow that can flow back from the shaft to the tank via the regulating valve must be shut off / reduced to a sufficiently small amount.

[0093] Injection regulating valves are usually designed such that they control / regulate the volume flow or the pressure on the piston side of the injection cylinder, which is coupled to the A-control port 502 of the regulating valve 1, for example. The injection cycle is divided into the following phases and is exemplarily shown in the volume flow-signal function in Figure 3 • "Injection" (via P-A control edge 20) • "Pressure regulation" with pressure reduction phase (via P-A control edge 20 and A-T control edge 21) • "Injection" (via P-A control edge 20) • "Suck-back" (via B-T control edge 22) • "Retraction movement" of the injection cylinder (via P-B control edge 23 and A-T control edge 21) Important for the process is the pressure regulation with pressure reduction phase. The pressure regulation is significantly influenced by the geometric coordination of the P-A control edge 20 and the A-T control edge 21.

[0094] Figure 1 The geometry of the control slide valve 4 (i.e., the overlap of the individual control edges and the resulting volumetric flow-signal function) is adapted here to each application.

[0095] Figure 4 and Figure 5 The diagram uses pages 1 to 7 to illustrate the source... Figure 1 The geometry of the 4 / 3-way control valve, especially the overlap of the control sides. Figure 3 Correspondingly, the applied volumetric flow is schematically shown in the characteristic curves 201, 211, 221, and 231 of the control edges 20, 21, 22, and 23 at P1 to P7. Figure 4 The prior art control slide valve 4 is shown in a regulating operation with zero-intersection P1 having control sides 20, 21, which enables good adjustability. Figure 5 The same control spool 4 as in the prior art is shown, however, it is in the fail-safe position. (Compared to...) Figure 4 Compared to the position in the middle, the control slide valve 4 shifts to the right, causing the PA control edge 20 to overlap at P5. However, in this case, the AT control edge 21 reaches a less overlapped position at P4, and the passage between the T-control port and the A-control ports 501, 502 remains open. This is undesirable in the fail-safe position 25, and is achieved by means of the switchable control edge according to this disclosure ( Figures 6 to 14 To prevent this. Based on the under-overlapping position P4 on characteristic curve 211, such as... Figure 3 As shown, a volumetric flow is applied at AT control edge 21 and through Figure 3 No volumetric flow is applied at the x-axis overlap position P5 and fail-safe position 25 at PA control edge 20.

[0096] exist Figure 4 In the adjustment operation, the PA control edge 20 between the P control port and the A control ports 502 and 503, together with the AT control edge 21 between the A control port and the T control ports 502 and 501, has a small relative overlap. In particular, Figure 4 The control edges 20 and 21 are designed with zero intersection P1, therefore the small relative overlap of these two zero-intersection control edges 20 and 21 results in zero intersection. The BT control edge 22 between the B control port and the T-channel 505 on the B side has a large degree of overlap, see [reference]. Figure 3 , Figure 4 P3 in the diagram; and the PB control edge 23 between the P-control port and the B-control ports 503 and 504 largely overlaps, see also P3 in the diagram. Figure 3 , Figure 4 P2 in the example. Figure 3 and Figure 4As shown in P2, the PB control edge 23 overlaps, therefore there is no volumetric flow between the P-control port and the B-control ports 503 and 504. Figure 3 and Figure 4 The middle part is shown with the help of P1. Figure 4 The PA control edge and AT control edges 20 and 21 are shown with very small relative overlap, with zero intersection.

[0097] Figure 4 , Figure 5 The geometry of the control slide valve 4 is in Figure 3 This is also understandable in the volume flow-signal function. Figure 3 Showing during adjustment operation Figure 1 , Figure 2 and Figure 4 , Figure 5 The volume flow-signal function of the regulating valve and its control slide valve 4 is known in the prior art. Figure 3 The y-axis represents the volumetric flow rate Q, in liters per minute (Q [l / min]), while the x-axis represents the control valve stroke S, which corresponds to... Figure 1 The stroke of the control slide valve 4 is expressed as a percentage. The larger the percentage stroke S of the control slide valve, the more volumetric flow occurs through the corresponding passages of control ports T, A, P, and B, because these passages are released by control edges 20, 21, 22, and 23 through the displacement of the control slide valve 4.

[0098] exist Figure 3 In this context, -100% signifies a negative final position, corresponding to the maximum rightward displacement of the control spool valve 4 within the valve body 1. Conversely, a positive final position of +100% signifies the maximum leftward offset of the control spool valve 4 within the valve body 1. For example, at the corresponding maximum offset, a stop at the corresponding end prevents further offset of the control spool valve 4.

[0099] exist Figure 3 The diagram also shows the control spool valve stroke S and the resulting overlap of control edges 20, 21, 22, and 23, in such a way that characteristic curves 201, 211, 221, and 231 reflect volumetric flow (especially during fail-safe conditions in prior art control valves). In the fail-safe position 25 during the fail-safe condition, in... Figure 1 When the fail-safe valve 2, located between the pilot valve 3 and the valve body 1, is shut off, the control spool valve 4 occupies a defined, spring-centered position. This fail-safe position of the control spool valve 4... Figure 3 The middle is represented by the dashed line 25 and in Figure 5 The diagram is shown schematically.

[0100] With the help of Figure 1the corresponding adjustable mechanical stop 8 in the control chamber 12, 13 in the control slide 4 to adjust the control slide 4 such that Figure 3 the P-A control edge 20 of the control slide 4 in the overlap position, see Figure 3 the intersection point P5 of the fail-safe position 25 in the x-axis and shown in dotted lines in the control slide 4 in the overlap position, see Figure 4 the very low relative overlap or zero intersection of the P-A control edge and the A-T control edge 20, 21) occupies an underlap position with respect to the valve body 1, see Figure 3 and Figure 5 the intersection point P4 of the volume flow-signal function 211 and the fail-safe position 25 in the control slide 4. During the fail-safe situation, the B-T control edge 22 between the B control port and the T-channel 505 on the B side continues to underlap, see Figure 3 , Figure 5 P7 in the control slide 4; and the P-B control edge 23 between the P-control port and the B-control port 503, 504 always still overlaps, see also Figure 3 , Figure 5 P6 in the control slide 4.

[0101] Thus, Figure 1 the piston surface of the injection cylinder 17 in the control slide 4 is no longer subjected to the supply pressure. This makes it possible to avoid, for example, the injection cylinder from extending. At the same time, when the fluid is subjected to an external force, for example, when plasticizing is taking place or in the configuration operation, the fluid can escape from the injection cylinder via the open A-T control edge 21 when the injection cylinder is filled with plastic melt.

[0102] As already mentioned, according to the present disclosure, a steering mechanism is integrated into an existing regulating valve. To this end, good adjustability in the regulating operation should be achieved by a small relative overlap between the P-A control edge and the A-T control edge 20, 21, and in the fail-safe situation also by the underlap design of the A-T control edge and the P-A control edge separating the A-control port 502 from the T-control port 501 and at the same time from the P-control port 503.

[0103] Hitherto, only regulating valves with fast and precise regulation have been known in the prior art, which have been implemented, manufactured with control edges as shown in Figure 3 , Figure 4 and Figure 5 . That is, control edges, which in the ideal case have a small relative overlap or zero intersection of the A-T control edge and the P-A control edge 21, 20 (as shown in Figure 3 and Figure 4 ) in order to be able to achieve fast and precise regulation, and on the other hand in the fail-safe position 25 (as shown in Figure 3 and Figure 5The A-control port 502 is separated from the P-control port 503, i.e. with a full overlap of the P-A control edge 20, as shown. However, the prior art regulating valves with fast and precise regulation are not able to separate the T-control port 501 and at the same time the P-control port 503 from the A-control port 502 in the fail-safe position 25 to ensure the shaft of the injection unit 15 to be at rest.

[0104] This is due to the fact that hitherto in the prior art the geometry of the control spool of the regulating valve, in particular the width of the piston lobes 31, 32, 33, 34 and thus the length of the control edges 20, 21, 22, 23, is no longer able to change after the manufacture of the valve and during operation. This makes it possible in valves with good adjustability during the fail-safe situation at the fail-safe position 25 only to achieve the separation of the P-control port 503 from the A-control port 502, as shown in Figure 3 、 Figure 4 and Figure 5 instead of the desired simultaneous separation of the A-control port 502 from the P-control port and the T-control port 503, 501.

[0105] In order to make it possible for the width of the piston lobes of the control spool 4 to behave as if it could be increased or decreased during operation, Figures 6 to 14 a switchable control edge according to the present disclosure is shown. Figure 6 and Figure 7 in combination with Figure 8 schematically shows how the width of the piston lobes and thus the length of the A-T control edge and the P-A control edge can be switched between overlap and zero intersection.

[0106] Figure 6 The regulating valve in the prior art in Figure 6 is in active regulation. For this purpose, as shown in Figure 3 , a first control spool 400 comprises an axial bore 40 with a second control spool 41 and at least one first and second lateral bore 46, 47 in the first and second piston lobe 31, 32 of the first control spool 400. In addition to the first control edge 45 (A-T1) and the third control edge 44 (P-A), a second control edge 42, 43 (A-T2) is designed. The first and third control edges 45, 44 correspond to the A-T control edge and the P-A control edge 21, 22 (as described with reference to Figure 4 , Figure 5 and Figure 6 ). The second control spool 41 comprises a first and second piston lobe 411, 412 and regulates the flow or flow path through the lateral bores 46, 47 and the axial bore 40. The second control edge 42, 43 (A-T2) and the third control edge 44 (P-A) form a zero intersection at the same time (as by means of Figure 6(as shown in P8 and P11), so that when the second control slide valve is in the open position (e.g.) Figure 6 (As shown) to perform precise and rapid adjustments. The first control edge 45 (A-T1) in Figure 6 In the overlapping position, Figure 6 It is located at P10. Additionally... Figure 6 As shown: the second control edges 42, 43 (A-T2) and the third control edge 44 (PA) together have a small relative overlap, in this case even a very small relative overlap, see [link to relevant documentation]. Figure 6 Page 9 of the document. This makes it possible for: Figure 8 As shown at positions P8, P11, and P9, the characteristic curve 443 of the third control edge and the characteristic curve 452 of the dashed line converge on the x-axis with a positive control stroke S, thereby determining the first control slide valve 400 in... Figure 6 A leftward or rightward movement (see arrow symbol) immediately achieves volumetric flow between the T-control port and A-control ports 501, 502, or between the P-control port and A-control ports 503, 502. The volumetric flow between the T-control port and A-control ports 501, 502 is via transverse holes 46, 47 and axial hole 40, where the first control edge 45 (A-T1) is in an overlapping position. Therefore, rapid and precise adjustment is still possible despite this. Compared to the prior art, this is not achieved through the AT control edge (which may...) Figure 6 Instead of immediately adjusting via the first control edge 45 (A-T1) corresponding to this disclosure, adjustment is immediately performed via the second control edges 42, 43 (A-T2) which are unknown in the prior art.

[0107] Figure 7 The control slide valve 400 is in the fail-safe position during fail-safe conditions. The second control slide valve 41 is closed because the first piston protrusion 411 of the second control slide valve 41 prevents flow through the transverse orifice 46. Figure 7 and Figure 8 P12 in the diagram. Thus, the second control edges 42, 43 (A-T2) are in an overlapping position, and there is no flow between the T-control port and the A-control port 501 via the transverse holes 46, 47 and the axial hole 40. The first control edge 45 (A-T1) and the third control edge 44 (PA) are designed to also overlap in the fail-safe position. Figure 7 P13 and P14 in the diagram. This ensures that in fail-safe position 25 (see...) Figure 8) no volumetric flow can flow between the T-control port and the A-control ports 501, 502 and between the P-control port and the A-control ports 503, 502. There is no flow path through the lateral holes 46, 47 and the axial hole 40 and there is also no direct flow path from the A-control port 502 to the T-control port 501.

[0108] Figure 8 The volumetric flow - signal functions of the control edges according to the present disclosure are shown from Figure 6 and Figure 7 The x-axis shows the control spool stroke S of the first control spool 400 according to the present disclosure. The fail-safe position 25 extends through the origin and coincides with the y-axis. Figure 8 Two cases of the characteristic curve progression of the volumetric flow between the A-control port 502 and the T-control port 501 are shown.

[0109] In the first case, in the case of active regulation with the second control spool 41 open and the second and third control edges 42, 43, 44 (A-T2; P-A) open, the volumetric flow can be quickly and precisely regulated via the second control edge 42, 43 (A-T2) and the third control edge 44 (P-A). If Figure 6 the first control spool 400 is shifted to the right in the valve body 1, the volumetric flow between the T-control port 501 and the A-control port 502 increases (as shown by the characteristic curve 452 in Figure 8 ), in such a way that a flow path via the second control edge 42, 43 (A-T2) and the lateral holes 46, 47 and the axial hole 40 is created. From a certain degree of further rightward shift, the characteristic curve 452 no longer rises further, since the maximum flow via the second control edge 42, 43 is limited by the diameter of the lateral holes 46, 47 and the axial hole 40. However, at P16 in Figure 8 , the first control edge 45 (A-T1 ) opens and an additional flow path between the T-control port and the A-control ports 501, 502 is created, see characteristic curve 451. In Figure 6 , when the first control spool 400 is shifted to the left, i.e. to the right from P8, P11, P9 in Figure 8 , the flow path between the P-control port and the A-control ports 503, 502 opens, while the flow path between the T-control port and the A-control ports 501, 502 closes, as shown by the characteristic curve 443. Thus, the volumetric flow between the T-control port, the A-control ports and the P-control port 501, 502, 503 can be quickly and precisely regulated. The behavior of the characteristic curves 451 and 452 and the characteristic curve 443 thus correspond to the characteristic curves from Figure 3 and Figure 4the behavior of the characteristic curves 201 and 211 of the prior art.

[0110] In the second case, in the fail-safe case (with fail-safe position 25), the second control slide 41 is closed, as already described with reference to Figure 7 Thus, there is no flow path between the T-control port and the A-control ports 501, 502 via the second control edge 42, 43 (A-T2) and the characteristic curve 452 does not act in the fail-safe case. The volume flow is correspondingly close to zero (apart from the gap leakage), see P12 in Figure 8 In the fail-safe position 25, the first control edge and the third control edge 45, 44 are implemented to overlap, which is symbolically shown by the areas P13, P14 in Figure 7 and Figure 8 Thus, the flow path from the A-control port 502 to the T-control port 501 is inhibited at the fail-safe position during the fail-safe case in such a way that the first control edge 45 (A-T1) is designed to overlap sufficiently large. At the same time, the third control edge 44 (P-A) also overlaps. Thus, it can be ensured that the shaft is stationary, for example the shaft of the injection unit 15 is stationary.

[0111] Figure 9 An inner bore system in a control slide 400 according to the disclosure is shown. The inner bore system enables a flow between the T-control port and the A-control ports 501, 502 via the axial bore 40 and forms a second control edge 42, 43 (A-T2) between the T-control port and the A-control ports 501, 502. The inner bore system comprises the axial bore 40, the second control slide 41, and the leakage relief bores 51, 52, which second control slide controls the flow between the control ports A and T via the second control edge 42, 43 (A-T2) in combination with the first control slide 400.

[0112] Figure 9 A regulating valve according to the disclosure in the fail-safe case in the fail-safe position 25 (see Figure 8 ) is shown, in which the fail-safe valve is open. Here, the first control edge 45 (A-T1 control edge) and the third control edge 44 (P-A control edge) are designed to overlap at the same time. Figure 9During a fail-safe situation, the A-T1 control edge and the P-A control edge 45, 44 overlap to a large extent. This is possible, inter alia, because the second control spool 41 is positioned such that the flow path between the T-control port and the A-control port 501, 502 via the second control edge 42, 43 (A-T2) is blocked by the first piston nose 411 of the second control spool 41. Thus, the flow path from the A-control port 502 to the T-control port 501 is inhibited during the fail-safe situation in the fail-safe position in such a way that the A-T1 control edge 45 is designed to overlap sufficiently. At the same time, the third control edge 44 (P-A) also overlaps. Thus, it can be ensured that the shaft is at rest, for example the shaft of the injection unit 15.

[0113] At the same time, the second control spool 41 in the axial bore 40 controls the A-T2 control edge 42, 43 and thus regulates the flow between the T-control port and the A-control port 501, 502. In Figure 9 , the second control spool 41 is positioned such that the left piston nose 411 of the second control spool 41 blocks the first transverse bore 46. Thus, no exchange can take place between the T-control port and the A-control port 501, 502 via the axial bore 40 and the second control edge 42, 43 (A-T2).

[0114] In Figure 10 , no fail-safe situation occurs and the regulating valve according to the disclosure is in normal regulating operation. The position of the piston nose of the first control spool 400 is illustrated in such a way that the third control edge 44 (P-A) and the second control edge 42, 43 (A-T2) are exactly at the opening point in order to regulate the volume flow / pressure between the T-control port and the A-control port 501, 502 and the P-control port and the A-control port 503, 502. That is, in Figure 10 , the second control spool 41 is in the open position as already described with reference to Figure 6 . A further movement of the first control spool 400 in the valve body 1 to the left to the positive final position results in a flow of fluid from the P-control port 503 via the third control edge 45 (P-A) to the consumer (for example the injection unit 15) coupled to the A-control port 502 and an increase in pressure there. A reverse movement of the first control spool 400 to the right to the negative final position results in a flow of fluid from the consumer and thus a decrease in pressure, because the second control spool 41 is positioned in such a way that the second control edge 42, 43 (A-T2) is opened by displacing the first control spool 400 to the right and thus a flow path between the T-control port and the A-control port 501, 502 is created, which is Figure 6 and Figure 8 characteristic curve behavior.

[0115] Thus, for an observer not knowing the second control spool 41 and the second control edge (A-T2 control edge), the first control spool 400 according to the present disclosure appears from the outside as if the width of the piston nose 32, i.e. the length of the first control edge 45, (in the prior art) can be varied. Thus, for this observer, the width of the piston nose 32 of the first control spool 400 is switchable even after manufacturing in such a way that one of the two states according to the present disclosure can be assumed. Figure 6 and Figure 7 This is not possible with the prior art control spool 4 by means of Figures 1 to 5 as already shown with reference to Figures 3 to 5

[0116] Figure 10 shows the regulating valve in the regulating operation of the A-T2 control edge and the P-A control edges 42, 43, 44 according to the present disclosure. The second control spool 41 is in the open position with overlapping control edges 42, 43, i.e. the second control spool 41 is positioned such that when the second control edges 42, 43 are released by displacing the first control spool 400, a flow path between the T-control port and the A-control ports 501, 502 via the axial bore 40 can be possible. At this moment in time is shown on the characteristic curves 452 and 443 at positions P8, P11 and P9 on the x-axis of Figure 8 When full opening of the second control edges 42, 43 (A-T2) is reached, the flow path via the second control edges 42, 43 (A-T2) is limited in terms of maximum flow, because even when the opening of the second control edges 42, 43 (A-T2) is maximum, the flow is limited due to the size of the diameters of the axial bore 40 and the first lateral bore 46. Thus, starting from a certain stroke S to the right of the first control spool 400, the flow path via the first control edge 45 (A-T1) is additionally released. This is shown in Figure 8 by the characteristic curves 451 and 452 at positions P10 and P15 on the x-axis.

[0117] Figure 11 shows the regulating valve in the regulating operation of the first control edge 45 (A-T1) and the control edge 23 (P-B) according to the present disclosure. In combination with Figure 8 (especially the characteristic curves 451 and 231) it is shown that the first control spool 400 is moved to the right in the valve body 1 to a maximum negative final position, wherein the third control edge 44 is closed and the second control spool 41 is in the closed position. I.e. the flow between the T-control port and the A-control ports 501, 502 via the axial bore 40 is blocked. Instead of this, Figure 11 ​A direct flow path between the T-control port and the A-control port 501, 502 is shown in which the first control edge 45 (A-T1 control edge) is in the open position and the second control edges 42, 43 (A-T2 control edge) are closed by the second piston nose 412 of the second control spool 40. In Figure 8 The corresponding volume flow - signal characteristic curves at the position of the control spool stroke S = -100% and the characteristic curves 451 and 231 are shown schematically in

[0118] The small relative overlap between the second control edges 42, 43 (A-T2) and the third control edge 44 (P-A) is thus achieved in the second control spool opening case in the adjustment operation and enables a fast and precise adjustability of the volume flow / pressure in the A-control port 502, since a volume flow between the control ports T-A or P-A is already generated depending on the direction of action with a small first control spool offset.

[0119] At the same time, as shown in Figure 12 the first control spool 400 according to the disclosure can be brought to the left to the positive final position with the control spool stroke S = +100% and thus adjusts the flow between the P-control port and the A-control port 503, 502 and the B-control port and the T-control port 504, 501 via the T-channel 505 on the B side via the third control edge 44 (P-A) and the fifth control edge 22 (B-T). No flow between the T-control port and the A-control port 501, 502 occurs because Figure 12 the second control spool 41 in is positioned such that the first piston nose 411 keeps the second control edge (A-T2) closed and there is no flow between the T-control port and the A-control port 501, 502 via the axial bore 40 despite the second piston nose 412 being in the open position. In addition, the first control edge 45 (A-T1) and the second control edges 42, 43 (A-T2) are in the overlap position of the first control spool 400 due to the positive final position.

[0120] Figures 6 to 14 In Figure 8 the piston noses 411, 412 of the second control spool 41 are designed according to the disclosure such that upon moving to the negative final position of the first control spool 400, for example in

[0121] Thus, Figures 6 to 14One aspect shows how to achieve a zero intersection behavior with the fail-safe valves 2 and 61 activated and thus a fast and precise adjustability by a relatively small overlap between the second control edge 42, 43 (A-T2) and the third control edge 44 (P-A). On the other hand, with the fail-safe valves deactivated (i.e. during a fail-safe situation at the fail-safe position 25), the leakage can be reduced to a minimum (corresponding to a gap leakage) with a sufficiently large overlap of the first control edge 45 (A-T1) and the third control edge (P-A) 44 (see P12, P13 and P14 in Figure 7

[0122] Figure 13 The regulating valve system 100 according to the present disclosure is schematically shown in a longitudinal section, comprising a regulating valve and fail-safe valves 2 and 3 / 2-way fail-safe seat valve and a pilot valve 3. For the sake of simplicity, the valve electronics 11 and the displacement measurement system 10 are not shown here. The valve electronics 11 and the displacement measurement system 10 are schematically shown in Figures 16 to 19

[0123] The valve body 1 according to the present disclosure comprises a first control spool 400, which can also be alternatively referred to as a main control spool 400. The first control spool 400 is provided with an axial bore 40, in which a second control spool 41 is arranged. The second control spool 41 is also referred to as an inner control spool 41. The second control spool 41 is smaller than the first control spool 400. In particular, the diameter of the second control spool 41 is smaller than the diameter of the first control spool 400, so that the second control spool 41 is accommodated within the axial bore 40.

[0124] Figure 13 The valve body 1 in Fig. 5 shows from left to right in a longitudinal section a first control port 501, a second control port 502, a third control port 503 and a fourth control port 504 and a T-channel 505 on the B-side, which is linked to the first control port 501 by means of a connection passage and / or an annular channel. The first control port 501 is a T-control port 501. Thus, the T-channel 505 on the B-side corresponds to the T-control port 501 on the B-side. The second control port 502 is an A-control port 502. The third control port 503 is a P-control port 503. The fourth control port 504 is a B-control port 504.

[0125] The first control spool 400 and the valve body 1 form a first control edge 45, also referred to as an A-T1 control edge. The first control edge 45 regulates the flow rate of a first flow path between the T-control port 501 and the A-control port 502.​​

[0126] Furthermore, the first control spool 400 and the valve body 1 form a second control edge 42, 43, which is also referred to as A-T2 control edge. The second control edge 42, 43 regulates the flow via the additional flow path between the T-control port 501 and the A-control port 501. Here, the second control edge 42, 43 (A-T2) and the third control edge 44 (P-A) form a small relative overlap. The first control edge 45 (A-T1) between the control ports T and A has a sufficiently large overlap. This makes it possible that in the case of a failure safety situation only a very small volume flow flows between the control ports T and A. The volume flow is so small that it corresponds to a common gap leakage.

[0127] The second control edge 42, 43 (A-T2) between the control ports T and A has one or more first lateral bores 46, which are connected to the axial bore 40 of the first control spool and enable a flow. At the input or output, respectively, there are recessed annular channels and / or control windows 421, 431 (shown schematically in Figure 14 ) designed. This makes it possible that the second control edge (A-T2) 42, 43 can be specifically adapted in terms of manufacture exactly to the third control edge 44 (P-A control edge between the P-control port 503 and the A-control port 502) via the annular channels and / or via the control windows. It is thus ensured that the third control edge 44 (P-A) can form a zero intersection overlap and the second control edge 42, 43 (A-T2) can form a small overlap. The sum of the two overlaps results in a small relative overlap between the second control edge (A-T2) 42, 43 and the third control edge 44 (P-A). This has also been described with reference to Figure 6 , Figure 7 and Figure 8 .

[0128] In the first control spool 400, in the area of the A-control port 502, one or more additional second lateral bores 47 are arranged, which are likewise connected to the axial bore 40.

[0129] Depending on the position of the actuating piston 48, the second control spool 41 activates and / or deactivates the additional flow path through the lateral bores 46, 47 and the axial bore 40 between the T-control port and the A-control port 501, 502. By shifting the first control spool 41 to the left or to the right, the flow and the pressure via the second control edge 42, 43 (A-T2) are adjusted.

[0130] The second control spool 41 has pressure applied annular surfaces 491, 492. These annular surfaces are formed at the first piston nose 411 in the front region of the second control spool 41 and at the second piston nose 412 in the rear region of the second control spool 41. They are hydraulically balanced and thus a load pressure via the A-control port 502 does not cause the second control spool 41 to be unintentionally actuated.

[0131] Leakage into the rear chamber 50 of the second control spool 41 is discharged via the axial pressure relief hole 51, via the B-side T-channel 505 to the T-control port 501. To this end, the first control spool 400 has one or more third lateral holes 52 in the region of the B-side T-channel 505.

[0132] The second control spool 41 has a slot 53 at its right end pointing into the rear chamber 50. This slot 53 enables the discharge of leakage via the axial leakage pressure relief hole 51 even in the blocked state, which is formed coaxially to the axial hole 40 in the direction of extension.

[0133] Figure 14 A left-hand partial view of a regulating valve according to the present disclosure is shown in Figure 17 corresponding to a first control spool and a second control spool according to the present disclosure (as already described in Figures 6 to 13 ). The regulating valve actively regulates the third control edge 44 (P-A) and the second control edges 42, 43 (A-T2). The internal system is open, i.e. the second control spool 41 is positioned such that the first piston nose 411 and the second piston nose 412 of the second control spool 41 release a passage between the T-control port 501 and the A-control port 502 via the second control edges 42, 43 and the hole 40. Additionally, the fail-safe valves 2 and 61 are switched on.

[0134] The actuating piston 48 is kept open by the valve 61 arranged at the end cap chamber 54 of the end cap 57 by the control pressure pX against the compression spring 56, which is internally supported at the end cap 57 or stop 58 (shown in Figure 14 ).

[0135] The actuating piston 48 has a left-hand annular surface 60 and a right-hand annular surface 55. The spring chamber 59 and the left-hand annular surface 60 of the actuating piston 48 are relieved in the event of a failure by the second valve 61 (shown in the figures, for example, as a switchable 3 / 2 through fail-safe seat valve) such that the compression spring 56 presses the actuating piston 48 against the second control spool 41.

[0136] The spring chamber 59 of the actuating piston 48 is constantly de-pressurized in the direction of the tank via the T-control port 501. To achieve this, the spring chamber 59 is connected to the T-control port 501 of the valve body 1 via one and / or multiple holes 62. Alternatively, the spring can be de-pressurized via the Y-de-pressurization port 507 via additional holes and / or via a separate, leak de-pressurization port arranged at the end cap 57 (not shown in the figures). Figure 14

[0137] At the same time, the 3 / 2-way fail-safe valve 61 in the Figure 13 is electrically connected to the 4 / 2-way fail-safe valve 2. In the fail-safe case, both fail-safe valves are de-energized. The 4 / 2-way fail-safe valve 2 connects the left control chamber 12 and the right control chamber 13 of the first control spool 400 in the valve body 1 in the de-energized state of the fail-safe case and thus creates a hydraulic short circuit. Here, the first control spool 400 is placed in a defined fail-safe position via the larger spring 131 in the right control chamber 13. The compression spring 56 presses the first control spool 400 into the defined fail-safe position, for example corresponding to the fail-safe position 25 in the Figure 8 , by means of the actuating piston 48 and the second control spool 41.

[0138] The fail-safe position in the fail-safe case is characterized in that both the third control edge 44 (P-A) and the first control edge 45 (A-T1) occupy a sufficiently large overlap position. At the same time, the second control spool 41 closes the first transverse hole 46, so that the second control edges 42, 43 (A-T2) likewise sufficiently overlap. As a result, the first flow path between the control ports T and A and the second flow path between the control ports P and A and also the additional flow path between the control ports T and A are blocked.

[0139] The shaft diameter 63 of the actuating piston 48 (shaft of the actuating piston into the axial bore 40 of the first control spool 400 and actuation of the second control spool 41) has a smaller diameter than the first and second piston noses 411, 412 or the axial bore 40 of the second control spool 41. Axial deviations of the piston bore caused by tolerances can thus be compensated for.

[0140] The second control spool 41 has a right-hand stop 64 in the rear region, in the region of the rear chamber 50, for transmitting the spring force of an inner spring 65 to the first control spool 400 in the fail-safe case. Alternatively, this can also take place in the region of the end cap 57 via a nose in the front region of the second control spool 41 (not shown in the figures).

[0141] The second control spool 41 is actively kept open by the pX pressure in the normal regulation operation in the case of an open (i.e. 3 / 2-way seat valve energized) actuating piston 48.​

[0142] The actuating piston 48 is connected to the second control spool 41 via a connecting element 76 or coupling element. The coupling element can be a threaded rod in its embodiment to compensate for manufacturing-induced axial and angular deviations between the piston axis of the second control spool 41 and the actuating piston 48. The connecting element as a threaded rod is embodied, for example, in the form of a counterbalance rod with threads on both sides Figure 14 is not shown in the middle).

[0143] To this end, the actuating piston 48 has an axial bore 77 in which the counterbalance rod is mounted. The counterbalance rod is braced against the small inner control spool (41) by means of the right-hand locking nut 66 and against the actuating piston (48) by means of the left-hand locking nut 78. The locking nut 78 is case-hardened and simultaneously forms a mechanical stop.

[0144] An O-ring 79 seals the right-hand control chamber 86 of the end cap chamber 54 off from the spring chamber 59 in the end cap 57. The O-ring 79 sits in an undercut 84 and is thus axially fixed against displacement. Figure 14 The sealing in the middle can also be embodied in other ways.

[0145] The counterbalance rod 76 has a hex socket 82 at the left end with which the small inner control spool can be finely adjusted axially before the locking nut 78 is tightened.

[0146] The leakage relief holes 51, 52, 62 or control holes for the 3 / 2-way valve can optionally be equipped with partitions, which are screwed into the corresponding threads.

[0147] The actuating piston 48 and the second control spool 41 are heat-treated (case-hardened and tempered) and thus have a higher wear resistance.

[0148] The overlap and underlap of the control edges 42, 43, 44, 45 relative to one another and the opening point can be specifically increased or reduced for the application.

[0149] The second control spool 41 can alternatively be equipped with structural measures to compensate for flow forces, such as grooves, lugs or chamfers.

[0150] The geometry of the control edges 42, 43, 44, 45 is alternatively optimally coordinated with the specific application by means of angles, radii or control windows to adjust the corresponding flow properties of the T-control port, A-control port, P-control port, B-control port 501, 502, 503, 504.

[0151] In the end cap 57, which is arranged on the left side of the valve body 1, a thread 67 is machined, into which a hardened stop 58 is screwed, which serves to prevent wear. Thus, when the actuating piston 48 travels against the end stop in the final position, the end cap 57 is not damaged. Alternatively, the end cap 57 can be made completely or partially of a hardened material, or the area 68 in which the actuating piston 48 comes into contact with the end cap 57 can be partially hardened.

[0152] Alternatively, the mechanism of the second control spool can be arranged on the right side of the valve body 1 in order to correspondingly design the B-T1 control edge and / or the B-T2 control edge, but not the A-T1 control edge and / or the A-T2 control edge, as switchable. Further possible is a combination in which the second control spool 41 within the first control spool 400 is extended such that both the first control edge and / or the second control edge (A-T1, A-T2) and simultaneously the B-T1 control edge and / or the B-T2 control edge can be formed as switchable. A corresponding adaptation of the leakage pressure relief holes 51, 52, 62 is possible.

[0153] Furthermore, the actuating piston 48 can alternatively be supplied, operated and actuated by means of a 4 / 2-way (not shown), by means of the pX pressure. When the actuating piston 48 is operated externally by means of the pX pressure and the 4 / 2-way seat valve, opening and closing can be actively carried out by means of the pressure.

[0154] The second control edges 42, 43 (A-T2 control edges) can be finely adjusted in the control spool 400 via control windows (e.g. hard-milled, etched) or alternatively via a surrounding groove (hard-turned, ground) for the respective application case.

[0155] Figure 15 An alternative disclosure is shown, in which the axial leakage pressure relief hole 51 of the first control spool 400 can merge into a control slot 69 and / or a surrounding groove 70 at the fourth piston nose 34 of the first control spool 400, which connects the axial leakage pressure relief hole 51 with the Y pressure relief port 507 of the valve body 1. To this end, the control slot 69 is connected to the axial leakage pressure relief hole 51 via a fourth lateral hole 73, and in the valve body 1 a further lateral hole 74 is arranged which leads to the Y channel 72. Thus, the leakage from the main control spool 400 can also be pressure relieved towards Y.

[0156] Alternatively, an additional compression spring can be arranged in the left end cap chamber / control chamber 54, 12 between the end cap 57 and the first control spool 400 (not shown in the figures).

[0157] A displacement measurement system or a proximity switch can be arranged at the actuating piston 48 in order to inquire the position of the piston and to incorporate it into the machine safety concept of the superordinate level.

[0158] Alternatively, when the P-control port 503 of the valve body 1 is connected to the 3 / 2 port valve by means of a bore, respectively, the 3 / 2 port valve can be supplied via the P-control port and not via the X line (P = 0 bar, X = 0 bar) Figure 15 is not shown in the middle).

[0159] In another embodiment, the actuating piston can also be embodied as a rotary piston. The second control spool is then correspondingly designed as a rotary spool to open and close the internal system by its implementation of a rotary motion instead of a longitudinal motion (P = 0 bar, X = 0 bar) Figure 15 is not shown in the middle).

[0160] It should finally be noted that the description and the embodiments of the present application are not to be understood as being limiting in principle in terms of a specific physical implementation of the application. All features explained and shown in connection with the individual embodiments of the present application can be provided in different combinations in the subject matter of the present application in order to achieve their advantageous effects at the same time.

[0161] Figures 16 to 19 A regulating valve system 100 is shown in a schematic view with a valve electronics 11 and a displacement measuring system 10, which are arranged on the right side of the valve body 1. The valve electronics and the displacement measuring system serve to electronically regulate the first control spool 400. The second control spool 41 is not electronically regulated, but is hydraulically controlled via the fail-safe valve 61 in interaction with the end cap 57 (arranged on the left side of the valve body 1) and the actuating piston 48. Figure 16 A regulating valve system 100 according to the present disclosure is shown, in which the fail-safe valve 2, 61 is switched off during a fail-safe situation when the first control spool 400 is in the intermediate position and the second control spool 41 is in the closed position. Figure 17 A regulating valve system 100 according to the present disclosure is shown, in which the fail-safe valve 2, 61 is switched on and actively regulates the third control edge 44 (P-A) and the second control edges 42, 43 (A-T2) in the case of the second control spool 41 being in the open position. However, no volume flow flows through the second control edges 42, 43 (A-T2) or the third control edge 44 (P-A) in addition to the gap leakage, since they are just still closed and in zero overlap. Figure 18 A regulating system 100 according to the present disclosure is also shown and a regulating valve system 100 according to the present disclosure is shown, in which the fail-safe valve 2, 61 is switched on and actively regulated at the positive maximum end position of the control spool stroke S = +100%, at which the main control spool 400 is displaced to the left in the valve body 1 by the valve electronics 11. As a result, the third control edge 44 (PA) and the fifth control edge 22 (BT) are in an underlap position and a volume flow flows between the corresponding control ports. Figure 19Also shown is the regulation system 100 according to the present disclosure with the fail-safe valve 2, 61 switched on and the first control spool stroke S = -100% actively entering the negatively regulated end position. Here, the first control edge 45 (A-T1) is in the under-lapped position and thus enables a volume flow between the T-control port and the A-control port 501, 502. The fourth control edge 22 (P B) is in the under-lapped position, a volume flow flows between the P-control port and the B-control port 503, 504. The second control spool 41 is in the closed position due to the position of its second piston nose 412 and thus no volume flow flows between the T-control port and the A-control port 501, 502 via the second control edges 42, 43 (A-T2).

[0162] The scope of the present invention is given by the claims and is not limited to the features set out in the description and / or shown in the drawings.

[0163] List of reference signs 1 valve body, main stage 2 fail-safe valve, safety valve 3 pilot valve 4 control spool in the prior art 5 control edge (prior art) 6 control edge (prior art) 7 compression spring 8 adjustable disc, mechanical stop 9 control port X, T, A, P, B, Y 10 displacement measurement system 11 valve electronics 12, 13 control chamber 14 injection regulation valve, regulation valve in the prior art 15 injection unit 16 injection cylinder 17 cylinder chamber / cylinder surface 20 P-A control edge 21 A-T control edge 22 B-T control edge 23 P-B control edge 25 fail-safe position 31 first piston nose 32 second piston nose 33 third piston nose 34 fourth piston nose 40 axial bore 41 second control spool, inner control spool 42, 43 second control edge, A-T2 control edge 44 third control edge, P-A control edge 45 first control edge, A-T1 control edge 46 at least one first lateral hole 47 at least one second lateral hole 48 actuating piston 50 rear chamber 51 further axial hole, leak relief hole 52 at least one third lateral hole, leak relief hole 53 slot at the right end of the second control spool 54 end cap chamber 55 right side annular surface of the actuating piston 56 compression spring 57 end cap 58 stop 59 spring chamber 60 left side annular surface of the actuating piston 61 second valve, 3 / 2 way fail safe valve 62 one and / or more holes, leak relief hole 63 collar diameter or shaft diameter of the actuating piston 64 right side stop 65 inner compression spring 66 right side lock nut 67 threads in the end cap for the stop 68 area in the end cap 69 control slot for leak relief to the Y channel 70 circumferential groove 72 Y channel 73 at least one fourth lateral hole leading to the control slot for leak relief to the Y channel 74 further lateral hole 76 connecting element 77 axial hole 78 left side lock nut 79 O-ring 80 connection between the two T control ports, tank bridge 82 hexagon socket cap screw 84 undercut 86 right side control chamber of the end cap chamber 100 regulating valve system according to the disclosure 131 large spring in the right side control chamber 201 volume flow-signal characteristic curve of the P-A control edge 211 volume flow-signal characteristic curve of the A-T control edge 221 volume flow-signal characteristic curve of the B-T control edge 231 P-B control edge volumetric flow - signal characteristic curve 411 First piston nose of second control spool 412 Second piston nose of second control spool 400 First control spool 421, 431 Groove-like annular passage, control window 443 Third control edge, P-A control edge volumetric flow - signal characteristic curve 451 First control edge, A-T1 control edge volumetric flow - signal characteristic curve 452 Second control edge, A-T2 control edge volumetric flow - signal characteristic curve 491 Surface (annular) at left piston nose of second control spool 492 Surface (annular) at right piston nose of second control spool 501 T- control port, first control port 502 Control port A, second control port 503 Control port P, third control port 504 Control port B, fourth control port 505 T- passage on B side 506 Control port X 507 Relief port Y

Claims

1. A regulating valve with switchable control edges, comprising: - a valve body (1) with a first control spool (400) and at least one first and second control port (501; 502; 503; 504; 505) and at least one control edge (6; 44; 45), wherein the first control spool (400) has an axial bore (40) and in the axial bore (40) a second control spool (41) is designed, - an end cap (57) with an actuating piston (48), wherein the actuating piston (48) is designed to engage into the axial bore (40), and the actuating piston (48) is designed to displace the second control spool (41) in the axial bore (40).

2. The regulating valve according to claim 1, wherein between the actuating piston (48) and the second control spool (41) a connecting element (76) is designed to compensate for axial and angular deviations.

3. The regulating valve according to claim 1, wherein the valve body (1) and the first control spool (400) form a first control edge (45) and a second control edge (42, 43), wherein between the second control edge (42, 43) and a third control edge (44) a smaller relative overlap is formed and the first control edge (45) has a larger overlap.

4. The regulating valve according to any of the preceding claims, wherein the second control edge (42, 43) has a recess-like annular channel (421, 431) or at least one control window (421, 431).

5. The regulating valve according to any of the preceding claims, wherein the second control edge (A-T2; 42, 43) is connected to the axial bore (40) in the first control spool (400) via at least one first lateral bore (46).

6. The regulating valve according to any of the preceding claims, wherein the first control spool (400) forms at least one second lateral bore (47) in the port area of a second control port (502), in particular an A-control port, of the valve body (1), wherein the at least one second lateral bore (47) is connected to the axial bore (40).

7. The regulating valve according to any of the preceding claims, wherein the actuating piston (48) is designed to control a flow path via the second control edge (A-T2; 42, 43) by means of the second control spool (41).

8. The regulating valve according to any of the preceding claims, wherein the second control spool (41) has two surfaces (491; 492) of equal area size for hydraulic compensation.

9. The regulating valve according to any of the preceding claims, wherein the axial bore (40) of the first control spool (400) comprises a chamber (50) with an internal compression spring (65).

10. The regulating valve according to any of the preceding claims, wherein an axial pressure relief bore (51) is designed coaxially to the axial bore (40) and wherein in particular ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ The first control spool (400) has at least one third lateral hole (52) in the area of the T-channel (505) on the B side, which is connected to the axial pressure relief hole (51) and constitutes a leakage flow path.

11. The regulating valve according to any of the preceding claims, wherein The second control spool (41) forms a slot (53) on its right end face to discharge leakage.

12. The regulating valve according to any of the preceding claims, wherein The end cap (57) further comprises: - a valve (61), and - a spring chamber (59) with a compression spring (56) and a stop (58).

13. The regulating valve according to any of the preceding claims, wherein The spring chamber (59) is connected to the valve body (1) via a pressure relief hole (62).

14. Use of the regulating valve according to any of the preceding claims as an injection regulating valve for controlling an injection unit (15), in particular an injection unit of an injection molding machine.

15. A regulating valve system (100) comprising: - a pilot valve (3), - a failsafe valve (2), and - a regulating valve according to any of the preceding claims.

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