Rotary valve with fully interrupted, pairwise meshing face gear sections

Abstract

Rotary valve (1) for use in controlling or regulating a coolant flow in a motor vehicle, comprising a primary spur gear (3) driven by an actuator (2) and a secondary spur gear (4) driven by it, each coupled to a rotary valve, wherein the primary spur gear (3) and the secondary spur gear (4) are each provided with a first spur toothing (5) and a second spur toothing (6), wherein each spur toothing (5, 6) is circumferentially interrupted, the spur toothing (5, 6) of each spur gear (3, 4) is arranged in two axially offset planes and is circumferentially offset from each other per spur gear (3, 4) and meshes with each other in pairs.

Description

[0001] The invention relates to the partial adjustment of valve units by means of two gear pairs and the use of locking elements such as pressure pins. In particular, the invention relates to a rotary slide valve for use in controlling or regulating a cooling fluid flow in a motor vehicle.

[0002] DE 10 2021 124 081 A1 discloses a valve control device for a coolant circuit of a motor vehicle. US 4 749 004 A discloses an air damper control device.

[0003] DE 10 2017 204 553 A1 discloses a rotary slide valve with a toothed segment device.

[0004] DE 10 2014 200 844 A1 discloses an adjustment arrangement for a rotary slide valve.

[0005] DE 10 2006 059 029 A1 discloses a rotary slide valve with several cross-sectional adjustment elements.

[0006] In the field of thermal management for electrified vehicles, such as passenger cars or commercial vehicles, there are increasing requests for coolant control units that can control / regulate more than five inputs / outputs. Due to the high complexity of the switching positions, these cannot currently be implemented with a single valve adjustment unit, which is why the desired switching positions must be achieved using two valve adjustment units. However, two actuators are currently required, each of which adjusts a rotary valve. This is complex, particularly in terms of space requirements and costs.

[0007] It is the object of the present invention to eliminate or at least mitigate these disadvantages.

[0008] This is achieved according to the invention in a rotary slide valve by means of a primary spur gear that can be driven / driven (directly) via a (single) actuator and a secondary spur gear that can be driven / driven (directly / immediately) by the latter, which are each coupled to a rotary slide, in such a way that the primary spur gear and the secondary spur gear are each provided with a first spur gear and a second spur gear, wherein each spur gear is circumferentially interrupted, the spur gears of each spur gear are arranged in two axially offset planes and are circumferentially offset from one another for each spur gear and mesh with one another in pairs.

[0009] More precisely, for example, the first or second spur gear toothing of one spur gear meshes with the first or second spur gear toothing of the other spur gear.

[0010] In this way, an actuator can be dispensed with, yet complex fluid flow control and regulation can still be achieved. In particular, coolant can be effectively controlled and regulated even with five or more inputs and outputs.

[0011] The core idea is therefore to adjust two rotary valves with just one actuator. When the actuator is controlled, only the first rotary valve is adjusted, whereby the second rotary valve is then only controlled / adjusted selectively depending on the volume flow requirements. It is therefore important that the actuator is directly connected to the first valve unit. The first valve unit and a second valve unit have different axes of rotation. The two valve units are connected selectively via the gear sections. The gear sections of one valve unit are axially offset from one another and are located in different planes. This affects both valve units. Due to this constellation, only a specific gear section of one valve unit can mesh with a corresponding gear section of the other valve unit.

[0012] In operation, this is as follows: Initially, parts of the gear pairs are engaged and the actuator only adjusts the first valve unit. Then, a gear section of the second valve unit engages with a gear section of the first valve unit. This means that not only the first valve unit but also the second valve unit adjusts. This adjustment takes place as long as the said gear section of one valve unit engages with the said gear section of the other valve unit. To ensure the position of the second valve unit, a pressure pin is used which, as it snaps into place in the valve housing, also causes a slight twist due to its centering effect. This means that even when the second valve unit is adjusted slightly, contact between the said gear sections of the two valve units is not possible.

[0013] The second valve unit is now firmly positioned in its new position. The first valve unit can be freely adjusted without affecting the second valve unit.

[0014] In order to be able to adjust the second valve unit again, the first valve unit must be turned far enough so that the second gear pair (other gear section on the first valve unit and other gear section on the second valve unit) engages.

[0015] These gear sections now reconnect the two valve units, and the second valve unit can now be adjusted back to its original position. To maintain the position of the second valve unit, a pressure pin is used (again), or rather, the pressure pin itself, which also causes a slight twist during the snap-in process due to its centering effect.

[0016] This prevents contact between the second gear sections, even with a slight adjustment of the second valve unit. The second valve unit is now firmly fixed in this position. The first valve unit can be freely adjusted without adjusting the second valve unit. The first valve unit can now be rotated again by the actuator until the first gear sections of the two valve units engage again. Implementing this in a thermal management module is particularly effective.

[0017] Advantageous embodiments are the subject of the subclaims and are explained in more detail below.

[0018] It is advantageous if the first spur gear of the primary spur gear meshes with the first spur gear of the secondary spur gear in selected / predefined operating conditions and disengages in selected / predefined operating conditions. This ensures precise gear shifting.

[0019] For precise switching, it is also advantageous if the second spur gear of the primary spur gear meshes with the second spur gear of the secondary spur gear in selected / predefined operating conditions and is / comes out of engagement in selected / predefined operating conditions.

[0020] For complex control / regulation tasks, it is advantageous if the rotary slide valve is designed as a 5 / 4 valve or 4 / 2 valve.

[0021] Control / regulation algorithms can intervene particularly effectively if the primary spur gear is designed as a 5 / 4 rotary slide valve and / or if the secondary spur gear is designed as a 4 / 2 rotary slide valve.

[0022] An advantageous embodiment is also characterized in that the two switching positions of the rotary slide valve coupled to or forming the secondary spur gear, in particular of the 4 / 2-way valve, are locked via a detent on a valve housing. Pressure pins have also proven to be a cost-effective way to implement such a detent. These are, for example, sleeves with locking elements, such as bolts or balls, preloaded by springs.

[0023] In this context, it has also proven useful if the locking mechanism is designed in such a way that the meshing teeth are disengaged when locking.

[0024] A further development is also characterized in that the angular offset of the detent is matched to the angular circumference of the toothing in such a way that precise switching is enforced during operation.

[0025] If the detent for the two starting positions of the 4 / 2 valve is offset by 90° to each other / has an angular offset of 90° + / -3°, particularly advantageous embodiments can be designed.

[0026] The spur gear teeth of one spur gear mesh with the spur gear teeth of the other spur gear only at an adjustment of approximately 90°. Depending on the design, an 87° rotation may also be appropriate. The remaining 3° is achieved by the snap-in of the thrust pins.

[0027] The invention is explained in more detail below with the aid of a drawing. It shows: Fig. 1 shows a switching cycle of an embodiment of a rotary slide valve according to the invention, for example a 3 x 80 watt pump configuration with a single actuator and two connectable rotary slides, wherein there are two starting positions for the driven secondary spur gear and from this one starting position is moved to the other in 90°, 60°, 60° and 90° steps, whereby other angle values ​​are also possible, Fig. 2 a perspective view from the front of the rotary slide valve, as it is in its different switching positions in Fig. 1 is shown, Fig. 3 a view from behind of the rotary slide valve of the Fig. 1 and Fig. 2, Fig. 4 a perspective view of the valve housing of the rotary slide valve of the Fig. 1 to 3, and Fig. 5 to 10 a perspective view of the initial situation ( Fig. 5), the beginning of tooth engagement ( Fig. 6), the ending tooth engagement ( Fig. 7) first spur gear teeth of the two spur gears as well as the beginning and ending meshing of the other spur gear teeth of the two spur gears ( Fig. 8 and Fig. 9), supplemented by the return to the initial situation ( Fig. 10).

[0028] The figures are merely schematic and serve only to clarify the invention. Identical elements are designated by the same reference numerals.

[0029] In Fig. Figure 1 shows different switching positions of a first embodiment of a rotary slide valve 1 according to the invention. The rotary slide valve 1 shown in detail is intended for use in a passenger car, namely an electric vehicle.

[0030] As in Fig. As can also be clearly seen in Figure 3, the rotary slide valve 1 has only a single actuator 2 or can be driven by the single actuator 2, which, during operation, drives a primary spur gear 3. A secondary spur gear 4 is driven via the primary spur gear 3. In the illustrated embodiment, the primary spur gear 3 and the secondary spur gear 4 each form a corresponding rotary slide valve. In principle, the rotary slide valves can be coupled not only through an integral design, but also as separate components with the interposition of a gear.

[0031] The primary spur gear 3 and the secondary spur gear 4 have first spur gears 5 and second spur gears 6. In selected operating states, the first spur gear 5 of the primary spur gear 3 meshes with the first spur gear 5 of the secondary spur gear 4. In other selected operating states, the second spur gear 6 of the primary spur gear 3 meshes with the second spur gear 6 of the secondary spur gear 4.

[0032] In addition, there is at least one detent 7, which, for example, uses a pressure pin with a detent means that engages in a first recess 8 and a second recess 9 of a valve housing 10, as is particularly well known in Fig. 4 can be seen.

[0033] In the Fig. Figures 5 to 10 show selected situations of the position of the rotary slide valve 1.

[0034] However, it is particularly well illustrated Fig. 1 the invention. Thus, there is a first starting position of the rotary slide valve 1 at the left edge of the Fig. 1, in which none of the spur gear teeth 5 or 6 of one spur gear 3 meshes with the corresponding spur gear tooth 5 or 6 of the other spur gear 4. The secondary spur gear is in the first switching position. Subsequently, a rotation of 90° clockwise takes place. The spur gear teeth 5 and 6 of the two spur gears 3 and 4 remain disengaged. Ergo, only the primary spur gear 3 rotates 90° clockwise. The switching positions are shown schematically below the rotary slide valve 1. A cooling fluid flow between the connections A, B, C1, G and H (see primary spur gear side, labeled clockwise from the 3 o'clock position starting) and C, D, F and C1 on the secondary spur gear side (labeled clockwise from the 3 o'clock position starting) is shown schematically.

[0035] Upon further rotation of 60°, spur gears 5 and 6 are still not meshing, and only primary spur gear 3, i.e., the left rotary valve, rotates. In a subsequent 60° clockwise rotation, spur gears 5 and 6 of primary spur gears 3 and 4 are still not meshing.

[0036] However, this changes during the subsequent rotation of 90° clockwise, since the first spur gears 5 of the two spur gears 3 and 4 now engage with each other, forcing a forced rotation of the secondary spur gear 4 or the respective rotary valve.

[0037] Now the secondary spur gear 4 rotates. At the end of the 90° rotation, which can also end 1.5° or even 3° earlier or later, the Fig. 1 not shown, but in Fig.2 indicated detent 7. Ergo, a detent means detent in one of the two recesses 8 or 9. A forced rotational movement of the secondary spur gear 4 is thereby forced, which disengages the two first spur gears 5.

[0038] This now results in the second switching position, which is considered the new starting position. Upon a subsequent 90° counterclockwise rotation, the two spur gears 3 and 4 are disengaged again, causing only the primary spur gear 3 to rotate. Even after a first subsequent 60° counterclockwise rotation and a second subsequent 60° rotation, the primary spur gears 3 and 4 remain decoupled from each other, since neither the first spur gears 5 nor the second spur gears 6 are in engagement with each other.

[0039] However, this changes during the subsequent 90° counterclockwise rotation, since the second spur gears 6 of the first primary spur gear 3 and the secondary spur gear 4 now engage with each other, whereby a forced movement of the secondary spur gear 4 is forced by the primary spur gear 3.

[0040] The detent 7 engages again and forces the two second spur gears 6 to be released, whereby the original starting position is resumed. List of reference symbols 1 rotary slide valve 2 Actuator 3 Primary spur gear 4 secondary spur gear 5 first spur gearing 6 second spur gearing 7 Detent 8 first recess 9 second recess 10 valve housings

Claims

[1] Rotary slide valve (1) for use in controlling or regulating a cooling fluid flow in a motor vehicle, with a primary spur gear (3) which can be driven via an actuator (2) and a secondary spur gear (4) which can be driven thereby, which are each coupled to a rotary slide, wherein the primary spur gear (3) and the secondary spur gear (4) are each provided with a first spur gear (5) and a second spur gear (6), wherein each spur gear (5, 6) is circumferentially interrupted, the spur gears (5, 6) of each spur gear (3, 4) are arranged in two axially offset planes and are circumferentially offset from one another for each spur gear (3, 4) and mesh with one another in pairs. [2] Rotary slide valve (1) according to claim 1, characterized by that the first spur gear (5) of the primary spur gear (3) meshes with the first spur gear (5) of the secondary spur gear (4) in selected operating states and is disengaged in selected operating states. [3] Rotary slide valve (1) according to claim 1 or 2, characterized by that the second spur gear (6) of the primary spur gear (3) meshes with the second spur gear (6) of the secondary spur gear (4) and is disengaged in selected operating states. [4] Rotary slide valve (1) according to one of claims 1 to 3, characterized by that the rotary slide valve (1) is designed as a 5 / 4 valve or 4 / 2 valve. [5] Rotary slide valve (1) according to claim 4, characterized by that the primary spur gear (3) is designed as a 5 / 4 rotary slide valve. [6] Rotary slide valve (1) according to claim 4, characterized by that the secondary spur gear (4) is designed as a 4 / 2 rotary slide valve. [7] Rotary slide valve (1) according to one of claims 1 to 6, characterized by that the two switching positions of the rotary slide valve (1) coupled to or forming the secondary spur gear (4) are locked via a detent (7) on a valve housing (10). [8] Rotary slide valve (1) according to claim 7, characterized by that the locking mechanism (7) is designed in such a way that the meshing teeth are disengaged when locking.

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