Pneumatic valve device for a compressed air installation and a transmission control or clutch system comprising such a pneumatic valve device

Abstract

The present invention relates to a pneumatic valve device for a compressed air installation, in particular having a pneumatic cylinder, in particular for an automatic clutch system or an automatic transmission control and clutch system, the pneumatic valve device comprising: - a pneumatic solenoid valve (10), the pneumatic solenoid valve (10) comprising a housing (101), the housing (101) having a supply channel (430), a removal channel (440) and an exhaust channel (160), wherein - the housing (101) surrounds a valve chamber (500) in which a valve body (200) can be moved relative to an exhaust valve seat (300) and a supply valve seat (400) along a valve axis (A1) by means of an actuator against the force of a valve spring (420), wherein - in a first position (E), the valve body opens the valve chamber (500) and the exhaust valve seat (300) towards the exhaust channel (160), and in a second position (V), the valve body opens the supply channel (430) towards the supply valve seat (400) and the valve chamber (500). According to the invention, - the housing (101) comprises a diffuser (110), the diffuser (110) being connected to the exhaust valve seat (300) in the direction of the exhaust channel (160), wherein a cross-section of a diffuser channel (111) of the diffuser widens from the exhaust valve seat (300) to the exhaust channel (160), and - the diffuser channel (111) extends transversely to the valve axis (A1), and a net width (311) of an exhaust valve seat channel (310) is smaller than a second net width (131, 132, 133) of the diffuser channel (111).

Description

Field of the Invention

[0001] The present invention relates to a pneumatic valve device for a compressed air installation, in particular having a pneumatic cylinder, in particular for an automated clutch system or an automated transmission control and clutch system. The invention also relates to a transmission control or clutch system having such a pneumatic valve device, in particular for commercial vehicles, such as trucks or buses. Background Art

[0002] Such a pneumatic valve device particularly includes a pneumatic solenoid valve. The solenoid valve can be represented as a pneumatic solenoid valve operated electromagnetically, which uses, for example, a permanent magnet as part of an actuator in order to hold a valve body in a predetermined position and, in this way, to achieve different switching states under the control of compressed air. A pneumatic solenoid valve is known, for example, from WO97 / 44580A1 or from EP2818779A1.

[0003] In particular, such a pneumatic solenoid valve has a housing which has a supply channel, a consumption channel and an exhaust channel. Here, the housing, in particular having at least one inlet and at least one outlet, surrounds a valve chamber in which the valve body can be moved relative to an exhaust valve seat leading to the exhaust channel and relative to a supply valve seat leading to the supply channel along a valve axis by means of an actuator against the force of a valve spring. In this sense, the valve body or a similar valve element serves to open and close the valve.

[0004] In particular, the actuator can cooperate with the valve spring which, for example, exerts a force on the valve body in a direction opposite to the direction of action of the actuator and thereby determines whether the valve is open or closed, for example, in the energized state of a magnet. In a first position, the valve body can open the valve chamber and the exhaust valve seat leading to the exhaust channel, and in a second position, the valve body can open the supply channel leading to the supply valve seat and the valve chamber.

[0005] The maximum flow rate of compressed air through the pneumatic solenoid valve can be substantially limited by the net width of the valve channels, for example, by the net width of the exhaust valve seat channel.

[0006] Furthermore, the power consumption of the actuator affects the opening degree of the solenoid valve via its maximum consumable magnetic force and thus also affects the flow rate of the solenoid valve. This can mean that for a given flow rate, a conventional solenoid valve has a certain minimum size and minimum power consumption.

[0007] In principle, EP2818779A1 describes a solenoid valve having diffuser characteristics. Such a valve can be further improved.

[0008] It is desirable to improve or increase the flow rate of pneumatic solenoid valves, in particular in connection with use with pneumatic cylinders, in particular in transmission control or clutch systems, in particular during exhaust. In particular, this should be possible without significantly increasing the clear width of the valve channel and / or the power consumption of the actuator, so that a design that is as compact as possible can be achieved, and even with an improved or increased flow rate. The pneumatic solenoid valves known hitherto can be further improved in this respect. Summary of the invention

[0009] This is the significance of the present invention, the purpose of which is to describe a pneumatic valve device, which in particular has a pneumatic cylinder, in which the flow of the pneumatic solenoid valve is increased, in particular for use with a pneumatic cylinder, preferably in a transmission control or clutch system.

[0010] This object is achieved by a pneumatic valve device according to the invention which in particular has a pneumatic cylinder.

[0011] The pneumatic valve device, in particular with a pneumatic cylinder, is particularly used in an automatic clutch system or an automatic transmission control and clutch system, and comprises:

[0012] - a pneumatic solenoid valve comprising a housing having a supply channel, a consumption channel and an exhaust channel, wherein

[0013] The housing surrounds a valve chamber in which the valve body can be moved by means of an actuator against the force of a valve spring along a valve axis relative to an exhaust valve seat leading to the exhaust channel and relative to a supply valve seat leading to the supply channel, wherein

[0014] In the first position, the valve body opens the valve chamber and the exhaust valve seat to the exhaust channel, and in the second position, the valve body opens the supply channel to the supply valve seat and the valve chamber.

[0015] According to the invention, in a pneumatic valve device it is envisaged that the housing comprises a diffuser which adjoins an exhaust valve seat opening into an exhaust channel, wherein the cross section of the diffuser channel of the diffuser widens from the exhaust valve seat to the exhaust channel, and

[0016] The diffuser passage extends transversely to the valve axis, and a clear width of the exhaust valve seat passage is smaller than a second clear width of the diffuser passage.

[0017] The valve body is mounted so as to be movable along the valve axis relative to the exhaust valve seat and the supply valve seat against the force of a valve spring by means of an actuator, the valve body allowing two switching positions of the solenoid valve.

[0018] In other words, according to the concept of the present invention, it is envisaged that the exhaust passage is integrally incorporated into the housing, and the exhaust passage has a diffuser that laterally abuts the exhaust valve seat. Furthermore, the cross-section of the diffuser passage of the diffuser widens from the exhaust valve seat to the exhaust passage outlet, wherein the exhaust passage extends transversely to the valve axis. The net width of the exhaust valve seat passage is smaller than the second net width of the diffuser passage.

[0019] The present invention starts from the consideration that air is accelerated when the cross-section expands. This enables the solenoid valve to exhaust more quickly, even if the diameter of the exhaust valve seat passage remains at least the same. The present invention has recognized that the power consumption is affected by the opening from the exhaust valve seat to the exhaust passage outlet.

[0020] The present invention has recognized that by using a diffuser, an increased flow rate can be achieved, especially in order to be able to reduce the power consumption of the solenoid valve. Furthermore, the present invention has recognized that by a diffuser assembled transversely (especially orthogonally) to the valve axis, an increased flow rate becomes possible. By means of the air deflection generated by the diffuser mounted transversely (especially orthogonally) to the valve axis, and by the special shaping of the exhaust port with a diffuser leading to the exhaust passage, the flowing air from the exhaust valve seat to the exhaust passage is thus accelerated. This results in a significantly higher effective nominal exhaust width.

[0021] Furthermore, a flow rate with reduced power consumption can be achieved with less installation space. In particular, this installation space is suitable for the use of a pneumatic valve device in a compressed air installation, which pneumatic valve device is especially one having a pneumatic cylinder, especially for an automatic clutch system or an automatic transmission control and clutch system.

[0022] To achieve this purpose, the present invention also proposes a system, namely a pneumatic system, which includes: a pneumatic cylinder for a compressed air installation, especially for a transmission brake; and a pneumatic valve device according to the present invention, namely having a pneumatic solenoid valve, which includes a housing having a supply passage, a consumption passage, and an exhaust passage. According to the present invention, it is envisaged that the supply passage of the pneumatic solenoid valve is connected to the pressure chamber of the pneumatic cylinder for discharging compressed air and allowing compressed air to enter.

[0023] The supply passage of the pneumatic solenoid valve is advantageously connected to the pressure chamber of the pneumatic cylinder for exhausting in the first position of the valve body of the solenoid valve and allowing air to enter in the second position of the valve body of the solenoid valve.

[0024] To achieve this purpose, the present invention also proposes a transmission control or clutch system, namely including a pneumatic valve device according to the present invention and / or a system according to the present invention.

[0025] The preferred development of the present invention details advantageous possibilities for implementing the above concept within the scope of the said object and with regard to further advantages.

[0026] Preferably, the overall structure of the solenoid valve corresponds to the structure of a 3 / 2-way valve.

[0027] In the valve device, in the first position, the consumption passage is preferably open to the exhaust passage via the valve chamber, and the supply valve seat is closed. Additionally or alternatively, in the valve device, in the second position, the supply passage is preferably open to the consumption passage via the valve chamber, and the exhaust valve seat is closed.

[0028] Preferably, it is stipulated that: in the first position, the valve body opens the valve chamber towards the exhaust passage via the exhaust valve seat and blocks the supply passage. Furthermore, preferably, it is stipulated that: in the second position, the valve body opens the supply passage to the supply valve seat and blocks the exhaust passage via the exhaust valve seat.

[0029] The valve device advantageously has a wall surrounding the valve chamber in the housing, wherein the diffuser passage extends in this wall, so that the diffuser is integrally integrated into the housing. Advantageously, the diffuser passage extends transversely to the valve axis starting from the exhaust valve seat.

[0030] The exhaust valve seat preferably includes an exhaust valve seat passage having a first net width and an exhaust valve seat outlet having a second net width. Advantageously, the first net width and the second net width are below a certain value.

[0031] In particular, the net width of the exhaust valve seat can be greater than the nominal intake width of the supply passage. The exhaust valve seat preferably has an exhaust valve seat passage and an exhaust valve seat outlet, and the net width of each of the exhaust valve seat passage and the exhaust valve seat outlet is greater than the nominal intake width of the supply passage.

[0032] The first net width of the diffuser passage adjacent to the exhaust valve seat outlet has a first net width within the range between a first specific value and a second specific value; for example, the first specific value and the second specific value are in the range of millimeters.

[0033] The second net width of the diffuser passage adjacent to the first outlet of the exhaust passage has a second net width within the range between another first specific value and another second specific value; for example, the first another specific value and the second another specific value are in the range of millimeters.

[0034] Optionally, the diffuser passage can have a flow baffle element and / or a flow guiding element. The first net width of the diffuser passage adjacent to the exhaust valve seat outlet is preferably smaller than the second net width of the diffuser passage adjacent to the first outlet of the exhaust passage.

[0035] Along the valve axis, the exhaust valve seat has a length within a first specific length value and a second specific length value. Advantageously, the length of the diffuser channel transverse to the valve axis is within the first and second length values; preferably, the first and second length values are in the range of millimeters.

[0036] Advantageously, the inner wall of the diffuser channel is designed as a flow baffle element in the diffuser channel, opposite to the exhaust valve seat channel. In a preferred development, additionally or alternatively, a pin-shaped flow guiding element is mounted along the valve axis on the inner wall of the diffuser channel, opposite to the exhaust valve seat channel.

[0037] In one development, the flow baffle element can be a flow edge pointing in the direction opposite to the exhaust direction and towards the exhaust valve seat, in particular a flow tip or a flow web.

[0038] Preferably, the housing has an upper seal groove and a lower seal groove on the outer side, wherein the diffuser abuts in the plane between the upper seal groove and the lower seal groove.

[0039] In a preferred development, the diffuser channel has a first section with a cylindrical and / or frustoconical design. In a further development, the diffuser channel has a second section with a curved design, in particular in the form of a horn.

[0040] The valve chamber advantageously extends along the valve axis, and the diffuser channel extends radially with respect to the valve axis, in particular the diffuser channel extends radially and the sub-sections are aligned perpendicular to the valve axis. However, in principle, any alignment of the diffuser channel transverse to the valve axis (i.e., in particular inclined with respect to the valve axis or perpendicular to the valve axis) is advantageous.

[0041] In a preferred development, the diffuser has at least a diffuser channel with a first radial alignment along a first diffuser angle. In a preferred development, the diffuser has a diffuser channel with a first radial alignment along a first diffuser angle and a diffuser channel with a second radial alignment along a second diffuser angle. Advantageously, the first and second diffuser channels are opposite to each other and symmetric about the valve axis.

[0042] In another advantageous development, the diffuser channels are arranged annularly around the valve axis.

[0043] Embodiments of the present invention will be described below with reference to the accompanying drawings. These drawings are not necessarily to scale; rather, the drawings are executed in schematic and / or slightly distorted form where helpful for explanation. Regarding the teachings directly recognizable from the drawings, attention is drawn to the relevant prior art. It should be borne in mind here that many modifications and changes can be made in connection with the form and details of the embodiments without departing from the general concept of the present invention. The features of the present invention disclosed in the description, the drawings, and the claims may be necessary for the development of the present invention, either individually or in any desired combination. In addition, all combinations of at least two features disclosed in the description, the drawings, and / or the claims fall within the scope of the present invention. The general concept of the present invention is not limited to the exact form or details of the preferred embodiments shown and described below, nor to the subject matter that would be limited compared to the subject matter claimed in the claims. In cases where a dimensional range is specified, it is also intended to disclose values lying within the range mentioned as the limiting values, and they are allowed to be used and claimed in any way. For simplicity, the same reference numerals are used below for the same or similar components or components having the same or similar functions. Description of the Drawings

[0044] Other advantages, features, and details of the present invention will become apparent from the following description of the preferred embodiments and with reference to the drawings, in which:

[0045] Figure 1 is a symbolic representation of a transmission, which is an example of an AMT (Automated Manual Transmission) system that has a transmission brake and the symbol of a pneumatic solenoid valve inserted therein according to a preferred embodiment, and the pneumatic solenoid valve is a preferred example of a pneumatic valve device for a compressed air device;

[0046] Figure 2 In view (A), a first circuit diagram of a first arrangement of a pneumatic solenoid valve in the form of a 3 / 2-way valve according to a first embodiment is shown, and in view (B), a second circuit diagram of a second arrangement of a pneumatic solenoid valve in the form of a 3 / 2-way valve according to a second embodiment is shown, in each case, Figure 1 the AMT system shown has a preferred embodiment of a pneumatic valve device in each case;

[0047] Figure 3 In the first view (A), a pneumatic valve device is shown, which is in the form of one of the pneumatic solenoid valves and is in the form of a 3 / 2-way valve, which shows the exhaust position, in which, in the first position (E), the valve body opens the valve chamber and the exhaust valve seat leading to the exhaust passage, and

[0048] The pneumatic valve device is shown in the second view (B), which is in the form of one of the pneumatic solenoid valves here and in the form of a 3 / 2-way valve. In this pneumatic valve device, in the second position (V), the valve chamber and the supply valve seat are open from the supply passage towards the consumption passage;

[0049] Figure 4 The structure of the pneumatic valve device is shown, which is in the form of one of the pneumatic solenoid valves here and, according to a particularly preferred embodiment, in the form of a 3 / 2-way valve. In the first position (E), as Figure 3 shown in A, it is used for exhausting by means of a diffuser adjacent to the exhaust valve seat leading to the exhaust passage, wherein the cross-section of the diffuser passage of the diffuser widens from the exhaust valve seat to the exhaust passage. Detailed Description

[0050] Figure 1 Symbolically shown is a transmission with a transmission brake 900, which is an example of an automatic clutch system or an automatic transmission control and clutch system 1000; thus, in this case, there is a compressed air device in the form of a transmission brake 900 for the transmission 910.

[0051] Generally, torque (not specifically shown) is transmitted via a shaft (i.e., here the input shaft of the transmission 910) having a plurality of gear trains 920 to a countershaft, and from this countershaft to the output shaft. Here, the number of gear trains 920 on the shaft corresponds to the number of gear ratios. The transmission brake 900 can be configured, for example, as a brake 930, which is pneumatically actuated by means of two two-way valves or by means of a 3 / 2-way valve and is connected to the countershaft via a fixed transmission ratio. Specifically, referring Figures 2 to 4 to, this 3 / 2-way valve is explained by way of example as a pneumatic solenoid valve according to the concept of the present invention.

[0052] Here, the transmission 910 with the transmission brake 900 is only shown as an example and also includes at least one compressed air source 940, which serves as an energy storage for the pneumatically operated components. Generally, the transmission 910 is controlled in a certain way (not specifically shown) by a transmission actuator as the final control element and is acted upon by a gearshift lever unit via a cable harness for vehicle data associated with the gear ratio to be selected. In addition, the clutch is controlled by a clutch actuator as the final control element. As required, the AMT solenoid valve can be used as a clutch actuator, or as a gear actuator, or as a pilot valve for precisely piloting these components. For example, such an AMT solenoid valve can also be implemented as a pneumatic solenoid valve according to the concept of the present invention; correspondingly, for example, the following description of the 3 / 2-way valve can also be applied to such an AMT solenoid valve.

[0053] In this regard, the following description of the transmission control and clutch system 1000 (that is, in this case, such a system has a compressed air device in the form of a transmission brake 900 for a transmission 910, and this compressed air device has Figure 2 a pressure cylinder 700 and a pneumatic solenoid valve 10) is to be understood by way of example as an instance of many applications of the pneumatic valve device 100 for a compressed air device explained in this way herein.

[0054] In Figure 1 each case of the transmission control and clutch system 1000 shown (that is, in this case, such a system has a compressed air device in the form of a transmission brake 900 for a transmission 910), Figure 2 a preferred embodiment of the pneumatic valve device 100 is shown in each case, which has a pneumatic solenoid valve 10 in the form of a 3 / 2-way valve in the first embodiment in view (A), or two pneumatic solenoid valves each in the form of a 3 / 2-way valve in the second embodiment in view (B). In both embodiments, the pneumatic valve device 100 is implemented as a system with a pressure cylinder 700, for example for Figure 1 the transmission brake 900 shown in

[0055] The pneumatic solenoid valve in the form of a 3 / 2-way valve is shown in a pneumatic graphic symbol. This graphic symbol corresponds to the symbol of a 3 / 2-way valve that has an actuator 410 in the form of an electromagnet for actuating the valve body of the 3 / 2-way valve into two switching states against the force of a valve spring, which can be seen in the symbol of the pneumatic solenoid valve 10 as a 3 / 2-way valve.

[0056] The pneumatic solenoid valve 10 in the form of a 3 / 2-way valve has: a first inlet (1), hereinafter referred to as the "supply port"; and a second inlet (2), hereinafter referred to as the "consumption port"; and an outlet (3), hereinafter referred to as the "exhaust port".

[0057] Two possible switching positions of the valve are also shown in views (A) and (B). In the first position (E), the consumption port (2) is pneumatically connected to the exhaust port (3), while the supply port (1) is blocked. In the second position (V) of the valve, the exhaust port (3) is blocked, and a flow path between the supply port (1) and the consumption port (2) becomes possible in a parallel circuit.

[0058] In Figure 2 the valve device 100 has a pneumatic solenoid valve 10, which in turn has or is connected to a supply channel 430, a consumption channel 440, and an exhaust channel 160. As Figure 3 and Figure 4More specifically, the supply channel 430 and / or the consumption channel 440 and / or the exhaust channel 160 are integrally incorporated into the housing 101 of the pneumatic solenoid valve 10.

[0059] In Figure 2 View (A), the supply channel 430 of the pneumatic solenoid valve 10 is connected to the pressure chamber 710 of the pneumatic cylinder 700 for discharging compressed air and allowing compressed air to enter. In Figure 2 View (B), the supply channel 430 of the first pneumatic solenoid valve 10.1 (as shown in the left figure) is connected to the first pressure chamber 710 of the pneumatic cylinder 700 for discharging compressed air and allowing compressed air to enter, while the supply channel 430 of the second pneumatic solenoid valve 10.2 (as shown in the right figure) is connected to the second pressure chamber 720 of the pneumatic cylinder 700 for discharging compressed air and allowing compressed air to enter.

[0060] In particular, respectively, the first position E of the valve body of the solenoid valves 10, 10.1, 10.2 is set for exhaust, and the second position V of the valve body of the solenoid valves 10, 10.1, 10.2 is set for intake.

[0061] Specifically, in the valve arrangement 100 according to Figure 2 View (A), it is stipulated that compressed air flows from the compressed air source 940 (when it is turned on) into the consumption channel 440 in the shown switching state S1, and from there into the pneumatic cylinder 700, that is, into the pressure chamber 710, which is here called pressure chamber C1; switching state S1, (V).

[0062] In the case of exhaust, switching state S2, (E), the compressed air escapes from the pressure chamber 720 of the pneumatic cylinder 700 (here called the pressure and spring chamber C2) into the atmosphere via the exhaust channel 160.

[0063] For the applications here, for example, for the transmission brake 900 according to Figure 1 it is advantageous that the escape of compressed air can be significantly faster compared to the supply of compressed air. Since this pneumatic valve device 100 has a diffuser 110, symbolically represented here, on the exhaust channel 160, the piston K in the pneumatic cylinder 700, which is a spring-return cylinder, is pushed back faster by the solenoid valves 10, 10.1, 10.2 according to the inventive concept. Therefore, the originally usually used separate additional quick exhaust valve is no longer needed.

[0064] In accordance with Figure 2In the valve device 100 having first and second pneumatic solenoid valves 10.1, 10.2 of view (B), a double-acting pneumatic cylinder 700 is provided; that is, when the first solenoid valve 10.1 is actuated in the switching state S1, compressed air flows into the first pressure chamber 710 (here called pressure chamber C1) of the pneumatic cylinder 700; switching state S1, (V).

[0065] In this case, the compressed air is forced out of the chamber of the pneumatic cylinder 700 opposite the second pressure chamber 720 through the exhaust passage 160 of the second pneumatic solenoid valve 10.2; that is, switching state S2, (E). Embodiments according to the present invention help to avoid backpressure and enable rapid movement of the piston K in the pneumatic cylinder 700 and allow for faster exhaust. Therefore, more dynamic performance is possible. For example, when shifting is performed by means of the pneumatic cylinder 700 according to the Figure 2 arrangement in view (B), this can be achieved.

[0066] In a corresponding manner, in the opposite direction, the compressed air is forced out of the chamber of the first pressure chamber 710 of the pneumatic cylinder 700 through the exhaust passage 160 of the first pneumatic solenoid valve 10.1; that is, switching state S1, (E).

[0067] Figure 3 In views (A) and (B), the same pneumatic solenoid valve 10 in the form of a 3 / 2-way valve in each case is shown in the first and second switching positions, which is used, for example, to implement the first and second pneumatic solenoid valves 10.1, 10.2 described above in Figure 2 for the purpose of explaining the operating mode and construction of a pneumatic solenoid valve in the form of a 3 / 2-way valve. The two exemplary cross-sections of the solenoid valve 10 are both along the axial direction of the valve axis A1.

[0068] This shows the pneumatic solenoid valve 10, which includes a housing 101 having a supply passage 430, a consumption passage 440, and an exhaust passage 160, and is for a pneumatic valve device 100 of a compressed air device, particularly having a pneumatic cylinder 700, particularly for Figure 2 or Figure 1 an automatic clutch system or an automatic transmission control and clutch system 1000.

[0069] Here, the housing 101 surrounds a valve chamber 500 in which a valve body 200 can be moved along the valve axis A1 relative to an exhaust valve seat 300 leading to the exhaust passage 160 and relative to a supply valve seat 400 leading to the supply passage 430 by means of an actuator 410 against the force of a valve spring 420.

[0070] In the first position E, that is Figure 3View (A), the valve body opens the valve chamber 500 and the exhaust valve seat 300 leading to the exhaust passage 160, and in the second position V, namely Figure 3 View (B), the valve body opens the supply passage 430 leading to the supply valve seat 400 and the valve chamber 500.

[0071] According to the concept of the present invention, the housing 101 includes a diffuser 110 which is adjacent to the exhaust valve seat 300 leading to the exhaust passage 160, wherein the cross-section of the diffuser passage 111 of the diffuser widens from the exhaust valve seat 300 to the exhaust passage 160.

[0072] According to the concept of the present invention, the diffuser passage 111 advantageously extends transversely to the valve axis A1, and the net width 311 of the exhaust valve seat passage 310 is smaller than the second net widths 131, 132, 133 of the diffuser passage 111.

[0073] A further improvement of this solution according to the concept of the present invention lies in that the exhaust passage 160 and the diffuser 110 of the solenoid valve 10 are accommodated in the housing 101 of the solenoid valve 10. In addition, the exhaust valve seat 300 has an exhaust valve seat passage 310 and an exhaust valve seat outlet 312 (which is shown in more detail in Figure 4 ). Specifically, their net widths are greater than the nominal intake width of the supply passage 430. That is to say, more specifically, the exhaust valve seat 300 has an exhaust valve seat passage 310 and an exhaust valve seat outlet 312, the respective net widths of which are greater than the nominal intake width of the supply passage 430.

[0074] Therefore, in the synergistic effect of the air deflection from the exhaust valve seat 300 to the exhaust passage 160 and the diffuser 110 (i.e., as a result of the special arrangement and (where applicable) shaping of the exhaust passage 160), the acceleration of the flowing compressed air is achieved, resulting in a significantly greater effective nominal exhaust width. This can be clearly and detailedly explained from the following explanation.

[0075] Figure 3 In view (A), the first position (E) of a pneumatic solenoid valve in the form of a 3 / 2-way valve 10 is shown, in which the valve body 200 opens the valve chamber 500 via the exhaust valve seat 300 towards the exhaust passage 160. This "exhaust position" E corresponds to the pneumatic connection of the consumption port 2 and the exhaust port 3, as can be seen in Figure 3 view (A). In this case, the compressed air to be discharged flows from the consumption passage 440 through the valve chamber 500 and the exhaust valve seat 300 to the exhaust passage 160, and leaves the solenoid valve 10 through the first and second exhaust passage outlets 161, 162. Here, the actuator 410 must act against the force of the valve spring 420 in order to close the valve chamber 500 so as to isolate it from the supply valve seat 400, as already referred toFigure 2 as explained.

[0076] In Figure 3 the second position V shown in view (B), the supply passage 430 leading to the supply valve seat 400 and the valve chamber 500 is open. The compressed air to be discharged can flow from the supply passage 430 through the supply valve seat 400 and the valve chamber 500 to the consumption passage 440, and leave the solenoid valve 10 via this path, which corresponds to Figure 2 the circuit of the supply port 1 and the consumption port 2 shown in

[0077] In Figure 3 the two valve positions shown in views (A) and (B), the consumption passage 440 is open, regardless of the position of the valve body 200. Depending on the exhaust position E or the supply position V, the direction of the compressed air flow to be conveyed through the consumption passage 440 is changed, which is correspondingly indicated by the direction lines.

[0078] Figure 4 The basic construction of the solenoid valve 10 is shown, in which the diffuser 110 is illustratively depicted and reference is made to the construction of the exhaust passage 160. The exhaust passage 160 is integrally incorporated into the housing 101 and is located between the upper sealing groove 151 and the exhaust valve seat passage 310, which is centered on the valve axis A1 and has a net width 311. It is bounded by a wall 140 with respect to the valve chamber 500 and is formed by two regions, but for clarity, only the structure located on the left side of the valve axis A1 is described in further consideration below. In the case of this exemplary illustration, the right hand side of the solenoid valve has the same structure.

[0079] The first region of the exhaust passage 160 is called the diffuser 110. The diffuser 110 is formed by at least one diffuser channel 111, 112, the cross-section of which widens from the valve axis A1 towards the second net width of the diffuser channel, which is represented here by the second net width 133 visible on the left side and the second net width 134 visible on the right side. Here, the cross-section of the diffuser channel widens along a diffuser angle, which is represented here by the diffuser angle 121 visible on the left side and the diffuser angle 122 visible on the right side.

[0080] Within the exhaust passage 160, the second region of the exhaust passage directly adjoins the diffuser. The cylindrical exhaust passage outlets 161, 162 have the second net widths 133, 134 of the diffuser channels and are bounded radially by the wall 140.

[0081] In the illustrated embodiment, the diffuser 110 and the exhaust passage 160 are arranged orthogonally to the valve axis A1, because accommodating the medium outlet in the axial direction would impair the function of the solenoid valve due to installation space reasons. Generally speaking, the exhaust process has a larger cross-sectional area compared to the case of a conventional solenoid valve.

[0082] This design makes it possible for the medium to be discharged to vertically impact the wall of the exhaust passage after gushing out from the exhaust valve seat 300. This is achieved by arranging the flow baffle element 620 perpendicular to the exhaust valve seat passage 310 in order to keep the flow resistance of the solenoid valve as low as possible. In the development of the present invention, the flow resistance can also be reduced by a pin-shaped flow guiding element 621 installed at the same point.

[0083] List of reference numerals

[0084] 1 Supply port

[0085] 2 Consumption port

[0086] 3 Exhaust port

[0087] 10 Pneumatic solenoid valve, especially a 3 / 2-way valve

[0088] 100 Pneumatic valve device

[0089] 101 Housing

[0090] 110 Diffuser

[0091] 111 First diffuser channel

[0092] 112 Second diffuser channel

[0093] 121 First diffuser angle

[0094] 122 Second diffuser angle

[0095] 131 First net width of the first diffuser channel

[0096] 132 First net width of the second diffuser channel

[0097] 133 Second net width of the first diffuser channel

[0098] 134 Second net width of the second diffuser channel

[0099] 140 Wall

[0100] 151 Upper sealing groove

[0101] 152 Lower sealing groove

[0102] 160 Exhaust passage

[0103] 161 First exhaust passage outlet

[0104] 162 Second exhaust passage outlet

[0105] 200 Valve body

[0106] 300 Exhaust valve seat

[0107] 310 Exhaust valve seat passage

[0108] 311 Net width of the valve seat

[0109] 312 Valve seat outlet

[0110] 400 Supply valve seat

[0111] 410 Actuator

[0112] 420 Valve spring

[0113] 430 Supply passage

[0114] 440 Consumption passage

[0115] 500 Valve chamber

[0116] 620 Flow baffle element

[0117] 621 Pin-shaped flow guiding element with a flow edge

[0118] 700 Pneumatic cylinder

[0119] 710 First pressure chamber

[0120] 720 Second pressure chamber

[0121] 800 System of the pneumatic solenoid valve 10 with the pneumatic cylinder 700

[0122] Compressed air device in the form of a transmission brake

[0123] 900 Transmission

[0124] 910 Gear train

[0125] 920 Brake

[0126] 930 Compressed air source 940

[0128] 1000 Transmission control and clutch system in the transmission

[0129] A1 Valve axis

[0130] ER Exhaust direction

[0131] V Valve

[0132] E first position

Claims

1. A pneumatic valve device (100) for a compressed air installation, the pneumatic valve device (100) comprising: - a pneumatic solenoid valve (10), the pneumatic solenoid valve (10) including a housing (101) having a supply channel (430), a consumption channel (440) and an exhaust channel (160), wherein - the housing (101) surrounds a valve chamber (500) in which a valve body (200) can be moved relative to an exhaust valve seat (300) leading to the exhaust channel (160) and relative to a supply valve seat (400) leading to the supply channel (430) along a valve axis (A1) by means of an actuator against the force of a valve spring (420), wherein - in a first position (E), the valve body opens the valve chamber (500) and the exhaust valve seat (300) leading to the exhaust channel (160), and in a second position (V), the valve body opens the supply channel (430) leading to the supply valve seat (400) and the valve chamber (500), wherein, - the housing (101) includes a diffuser (110) adjacent to the exhaust valve seat (300) leading to the exhaust channel (160), wherein the cross-section of the diffuser channels (111, 112) of the diffuser (110) widens from the exhaust valve seat (300) to the exhaust channel (160), wherein the diffuser channels (111, 112) have a first section with a frustoconical design, and / or - the diffuser channels (111, 112) have a second section with a curved design, and - the diffuser channels (111, 112) extend transversely to the valve axis (A1) starting from the exhaust valve seat (300), and the net width (311) of the exhaust valve seat channel (310) is smaller than the net width (131, 132, 133, 134) of the diffuser channels (111, 112), and - in the diffuser channels (111, 112), a flow baffle element (620) is designed as a pin-shaped flow guiding element (621) on the valve axis (A1) opposite the exhaust valve seat channel (310).

2. The pneumatic valve device (100) according to claim 1, characterized in that - in the first position, the consumption channel (440) is open to the exhaust channel (160) via the valve chamber (500), and the supply valve seat (400) is closed, and - in the second position, the supply channel (430) is open to the consumption channel (440) via the valve chamber (500), and the exhaust valve seat (300) is closed.

3. The pneumatic valve device (100) according to claim 1 or 2, characterized in that The housing (101) has a wall (140) surrounding the valve chamber (500), wherein the diffuser channel (111) extends in the wall, and thus, the diffuser (110) is integrally incorporated into the housing (101).

4. The pneumatic valve device (100) according to claim 1, characterized in that the exhaust valve seat (300) comprises: an exhaust valve seat channel (310) having the net width (311) as a first net width; and an exhaust valve seat outlet (312) having a second net width.

5. The pneumatic valve device (100) according to claim 4, characterized in that the net width (311) of the exhaust valve seat channel (310) is greater than the nominal intake width of the supply channel (430).

6. The pneumatic valve device (100) according to claim 5, characterized in that the exhaust valve seat (300) has the exhaust valve seat channel (310) and the exhaust valve seat outlet (312), and each of the net width (311) of the exhaust valve seat channel (310) and the second net width of the exhaust valve seat outlet (312) is greater than the nominal intake width of the supply channel (430).

7. The pneumatic valve device (100) according to claim 4, characterized in that the net width (131) of the diffuser channels (111, 112) adjacent to the exhaust valve seat outlet (312) is less than the net width (133, 134) of the diffuser channels (111, 112) adjacent to the first outlets (161, 162) of the exhaust channel (160).

8. The pneumatic valve device (100) according to claim 1, characterized in that a first region of the exhaust channel (160) is formed as the diffuser (110), and a second region of the exhaust channel (160) directly adjoins the diffuser (110) and is formed as a cylindrical exhaust channel outlet (161, 162).

9. The pneumatic valve device (100) according to claim 1, characterized in that the diffuser (110) is formed by a first diffuser channel (111) and a second diffuser channel (112), and the cross-sections of the first and second diffuser channels (111, 112) widen from the valve axis (A1) towards the net widths (133, 134) of the first and second diffuser channels (111, 112), which net widths are represented by the net width (133) visible from the left and the net width (134) on the right.

10. The pneumatic valve device (100) according to claim 1, characterized in that - the inner wall of the diffuser channel is designed as the flow baffle element (620) in the diffuser channels (111, 112) opposite to the exhaust valve seat channel (310).

11. The pneumatic valve device (100) according to claim 1, characterized in that the flow baffle element (620) has a flow edge pointing in a direction opposite to the exhaust direction and towards the exhaust valve seat (300).

12. The pneumatic valve device (100) according to claim 11, characterized in that the flow baffle element (620) has a flow tip or a flow web.

13. The pneumatic valve device (100) according to claim 1, characterized in that the housing (101) has an upper seal groove (151) and a lower seal groove (152) on the outer side, wherein the diffuser (110) abuts in a plane between the upper seal groove (151) and the lower seal groove (152).

14. The pneumatic valve device (100) according to claim 1, characterized in that the curved design is in the form of a horn.

15. The pneumatic valve device (100) according to claim 1, characterized in that the valve chamber (500) extends along the valve axis (A1), and the diffuser channels (111, 112) extend radially.

16. The pneumatic valve device (100) according to claim 15, characterized in that the diffuser channels (111, 112) extend radially such that sub-segments are aligned perpendicular to the valve axis.

17. The pneumatic valve device (100) according to claim 1, characterized in that the diffuser (110) has at least a diffuser channel (111) radially aligned along a first diffuser angle (121).

18. The pneumatic valve device (100) according to claim 17, characterized in that the diffuser (110) has a diffuser channel (111) radially aligned along a first diffuser angle (121) and a diffuser channel (112) radially aligned along a second diffuser angle (122).

19. The pneumatic valve device (100) according to claim 18, characterized in that the first radially aligned diffuser channel (111) and the second radially aligned diffuser channel (112) are positioned opposite to each other and symmetric about the valve axis (A1).

20. The pneumatic valve device (100) according to claim 1, characterized in that the diffuser channels (111, 112) are arranged annularly around the valve axis (A1).

21. The pneumatic valve device (100) according to claim 1, characterized in that the compressed air device is suitable for an automatic clutch system or an automatic transmission control and clutch system (1000) and has a pneumatic cylinder.

22. A pneumatic system (800) comprising a pneumatic cylinder (700) for a compressed air device and a pneumatic valve device according to any one of claims 1 to 20, the pneumatic valve device having a pneumatic solenoid valve (10), the pneumatic solenoid valve (10) comprising a housing (101), the housing (101) having a supply channel (430), a consumption channel (440) and an exhaust channel (160), wherein the supply channel (430) of the pneumatic solenoid valve (10) is connected to the pressure chamber of the pneumatic cylinder (700) for discharging and allowing compressed air to enter.

23. The pneumatic system (800) according to claim 22, characterized in that The supply passage (430) of the pneumatic solenoid valve (10) is connected to the pressure chamber of the pneumatic cylinder (700) for discharging compressed air at the first position (E) of the valve body of the solenoid valve (10) and for allowing compressed air to enter at the second position (V) of the valve body of the solenoid valve (10).

24. The pneumatic system (800) according to claim 22, wherein, the compressed air device is a transmission brake (900).

25. A transmission control or clutch system (1000) comprising the pneumatic valve device (100) according to any one of claims 1 to 21 or the system according to claim 22 or 23 or 24.

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