DE102022114790A1 - Rotary valve with circumferentially interrupted, meshing pairs of spur gear sections and thermal management module with rotary valve - Google Patents

Abstract

The invention relates to a rotary valve (1) for use in controlling or regulating a cooling fluid flow in a motor vehicle, with a primary spur gear (3) that can be driven (directly) via an actuator (2) and a secondary spur gear (4) that can be driven (directly) by it are each coupled to a rotary slide valve, wherein both 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), each spur gear (5, 6) being interrupted circumferentially , 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 per spur gear (3, 4) and mesh with one another in pairs.

Description

The invention relates to the partial adjustment of valve units by two pairs of gears and the use of locking elements such as pressure pins.

In particular, the invention relates to a rotary valve for use in controlling or regulating a cooling fluid flow in a motor vehicle.

In the area of thermal management for electrified motor vehicles, such as 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, they can currently no longer be implemented using one valve adjustment, which is why the desired switching positions must be implemented using two valve actuating units. However, so far two actuators have always been required, each of which adjusts a rotary slide.

This is complex, especially in terms of space requirements and costs.

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

In the case of a rotary valve, this is achieved according to the invention by means of a primary spur gear that can be driven (directly) via a (single/sole) actuator and a secondary spur gear that can be driven (directly/immediately) thereof, each of which is coupled to a rotary slide valve, in such a way that both the primary spur gear and the secondary spur gear are each provided with a first spur gear and a second spur gear, each spur gear being circumferentially interrupted, the spur gears of each spur gear are arranged in two axially offset planes and are circumferentially offset from one another per spur gear and mesh with one another in pairs.

More precisely, for example, the first or second spur gearing of one spur gear meshes with the first or second spur gearing of the other (/second) spur gear.

In this way, an actuator can be dispensed with and complex fluid flow control/regulation can still be achieved. In particular, coolant, such as coolant, can be easily controlled/regulated even with five or more inputs/outputs.

The core idea is therefore to adjust two adjustment valves with just one (single) actuator. When controlling the (sole) (stand-alone) actuator/actuator, only the first adjustment valve is always adjusted, with the second adjustment valve then only being activated/adjusted selectively depending on the volume flow requirements. It is therefore important that the actuator is connected directly 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 at certain points via the gear sections. The gear sections of a valve unit are axially displaced relative to 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.

• Zunächst sind Teile der Zahnradpaare im Eingriff und der Aktor verstellt nur die erste Ventileinheit. Anschließend ist ein Zahnradabschnitt der zweiten Ventileinheit in Eingriff mit einem Zahnradabschnitt der ersten Ventileinheit. Somit verstellt sich neben der ersten Ventileinheit auch die zweite Ventileinheit. Diese Verstellung erfolgt so lange, wie der besagte Zahnradabschnitt der einen Ventileinheit mit dem besagten Zahnradabschnitt der anderen Ventileinheit in Eingriff steht. Um die Position der zweiten Ventileinheit zu gewährleisten, wird ein Druckstift verwendet, der während des Einschnappens im Ventilgehäuse ebenso durch die Zentrierwirkung ein leichtes Verdrehen bewirkt. Somit ist auch bei leichter Verstellung der zweiten Ventileinheit keine Berührung der besagten Zahnradabschnitte der beiden Ventileinheiten möglich.

In operation this is as follows:

• Initially, parts of the gear pairs are in mesh and the actuator only adjusts the first valve unit. A gear section of the second valve unit is then in engagement with a gear section of the first valve unit. In addition to the first valve unit, the second valve unit is also adjusted. This adjustment takes place as long as said gear section of one valve unit is in engagement with said gear section of the other valve unit. In order to ensure the position of the second valve unit, a pressure pin is used, which also causes slight rotation due to the centering effect when it snaps into the valve housing. This means that even if the second valve unit is slightly adjusted, the said gear wheel sections of the two valve units cannot come into contact.

The second valve unit is now firmly positioned in the new position. The first valve unit can be freely adjusted without adjusting the second valve unit.

In order to be able to adjust the second valve unit again, the first valve unit must be rotated to such an extent that the second gear pair (other gear section on the first valve unit and other gear section on the second valve unit) comes into engagement.

Through these gear sections, the two valve units are now connected again and the second valve unit can now be moved back to the starting position. To ensure the position of the second valve unit, a pressure pin is used (again) or the pressure pin is used det, which causes slight twisting during snapping due to the centering effect.

This means that even when the second valve unit is slightly adjusted, no contact with the second gear wheel sections is possible. 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. Now the first valve unit can be rotated again by the actuator so that the first-mentioned gear wheel sections of the two valve units come into engagement again. The implementation in a thermal management module is particularly effective

Advantageous embodiments are claimed in the subclaims and are explained in more detail below.

It is therefore advantageous if the first spur gearing of the primary spur gear meshes with the first spur gearing of the secondary spur gear in selected/predefined operating states and comes/is out of engagement in selected/predefined operating states. In this way, precise switching can be guaranteed.

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

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

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.

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

In this context, it has also proven useful if the detent is designed in such a way that the meshing teeth are disengaged/forced to disengage during the detent.

A further development is also characterized in that the angular offset of the detent is coordinated with the angular circumference of the toothing in such a way that precise switching is forced during operation.

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

The spur gearing of one spur gear only engages with the spur gearing of the other spur gear from an adjustment of approx. 90°. Depending on the design, an 87° rotation can also make sense. The remaining 3° are done by snapping/folding in the pressure pins.

The invention is explained in more detail below with the aid of a drawing.

• 1 einen Schaltzyklus einer erfindungsgemäßen Ausführungsform eines Drehschiebers, beispielsweise eine 3 mal 80 Watt Pumpenkonfiguration mit einem einzigen Aktor und zwei koppelbaren Drehschieberventilen; wobei es zwei Startpositionen für das angetriebene Sekundärstirnrad gibt und von diesem in 90°-, 60°-, 60°- und 90°-Schritten von der einen Startposition zur anderen gelangt wird, wobei auch andere Winkelwerte möglich sind,
• 2 eine perspektivische Darstellung von vorne auf den Drehschieber, wie er in seinen unterschiedlichen Schaltstellungen in der 1 dargestellt ist,
• 3 eine Ansicht von hinten auf den Drehschieber der 1 und 2,
• 4 eine perspektivische Darstellung des Ventilgehäuses des Drehschiebers der 1 bis 3, und
• 5 bis 10 eine perspektivische Darstellung der Ausgangssituation (5), des beginnenden Zahneingriffes (6), des endenden Zahneingriffes (7) erster Stirnverzahnungen der beiden Stirnräder, sowie den beginnenden Zahneingriff sowie den endenden Zahneingriff der anderen Stirnverzahnungen der beiden Stirnräder (8 und 9), ergänzt durch die Rückkehr in die Ausgangssituation (10).

Show it:

• 1 a switching cycle of an embodiment of a rotary valve according to the invention, for example a 3 x 80 watt pump configuration with a single actuator and two connectable rotary valves; where there are two starting positions for the driven secondary spur gear and this moves from one starting position to the other in 90°, 60°, 60° and 90° steps, with other angle values also being possible,
• 2 a perspective view from the front of the rotary valve as it appears in its different switching positions in the 1 is shown,
• 3 a view from behind of the rotary valve 1 and 2 ,
• 4 a perspective view of the valve housing of the rotary valve 1 until 3 , and
• 5 until 10 a perspective representation of the initial situation ( 5 ), the beginning of tooth engagement ( 6 ), of the ending tooth mesh ( 7 ) first spur gears of the two spur gears, as well as the beginning tooth mesh and the ending tooth mesh of the other spur gears of the two spur gears ( 8th and 9 ), supplemented by the return to the initial situation ( 10 ).

The figures are only schematic in nature and only serve the inventor's understanding dung. The same elements are given the same reference numbers.

In the 1 Different switching positions of a first embodiment of a rotary valve 1 according to the invention are shown.

Such a rotary valve 1 is also good 1 shown in excerpts. The rotary valve 1 is intended for use in a passenger car, namely an electric vehicle/e-vehicle.

As in 3 Also clearly visible, the rotary valve 1 only has a single / sole actuator / actuator or can be driven by a single actuator, which is referenced with the reference number 2.

That actuator 2 drives a primary spur gear 3 during operation. A secondary spur gear 4 is driven during operation via the primary spur gear 3. In the embodiment shown, the primary spur gear 3 forms a corresponding rotary slide valve. The secondary spur gear 4 forms a corresponding rotary slide valve. In principle, the rotary slide valves can also be coupled not only through an integral design, but also as separate components with the interposition of a gear.

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 gearing 5 of the primary spur gear 3 meshes with the first spur gearing 5 of the secondary spur gear 4. In other selected operating states, the second spur gearing 6 of the primary spur gear 3 meshes with the second spur gearing 6 of the secondary spur gear 4.

In addition, there is at least one detent 7, which uses, for example, a pressure pin which has a blocking/locking means which is inserted into a first recess 8 and a second recess 9 of a valve housing 10, as is particularly well shown in 4 can be seen, clicks into place.

In the 5 until 10 Selected situations of the position of the rotary valve 1 are shown.

However, this illustrates particularly well 1 The invention. There is a first starting position of the rotary slide 1 on the left edge of the 1 , in which none of the spur gears 5 or 6 mesh with the corresponding spur gears 5 or 6 of one spur gear 3 with the other spur gear 4. The secondary spur gear is in the one (first) switching position. A rotation/rotation of 90° clockwise then takes place. The spur gears 5 and 6 of the two spur gears 3 and 4 remain out of engagement. Ergo, only the primary spur gear 3 rotates 90° clockwise. The switching positions are shown schematically under the rotary valve 1. A cooling fluid flow between the ports A, B, C1, G and H (see primary spur gear side named starting from the 3 o'clock position clockwise) and C, D, F and C1 secondary spur gear side (named starting from the 3 o'clock position clockwise) is shown schematically .

With a further rotation of 60°, there are still no spur gears 5 and 6 in mesh with one another and only the primary spur gear 3, i.e. the left rotary slide valve, rotates. In a subsequent 60° clockwise rotation, the spur gears 5 and 6 of the primary spur gears 3 and 4 are still not in engagement with one another.

However, this changes with the subsequent rotation of 90° clockwise, since the first spur gears 5 of the two spur gears 3 and 4 now engage with one another, whereby a forced rotation of the secondary spur gear 4, or the associated rotary slide valve, is forced.

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

Now the position of the second switching position takes place, which is considered the new starting position. During a subsequent rotation of 90° in the counterclockwise direction, the two spur gears 3 and 4 are disengaged again, as a result of which only the primary spur gear 3 rotates. Even after a first subsequent 60° counterclockwise rotation and a second subsequent 60° rotation, the primary spur gears 3 and 4 still remain decoupled from one another, since neither the first spur gears 5 nor the second spur gears 6 are in engagement with one another.

However, this changes with 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 one another, whereby a forced movement of the secondary spur gear 4 is forced by the primary spur gear 3.

The detent 7 engages again and forces the two second spur teeth 6 to loosen, whereby the original starting position is assumed again.

Reference character list

1

Rotary valve

2

Actuator / actuator

3

primary spur gear

4

Secondary spur gear

5

first spur gearing

6

second spur gear

7

Detent

8th

first recess

9

second recess

10

Valve housing

Claims (8)

Rotary slide valve (1) for use in controlling or regulating a cooling fluid flow in a motor vehicle, with a primary spur gear (3) that can be driven (directly) via an actuator (2) and a secondary spur gear (4) that can be driven (directly) by it, each with a Rotary slide valve are coupled, wherein both 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), each spur gear (5, 6) being 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 per spur gear (3, 4) and mesh with one another in pairs. Rotary slide (1) forward Claim 1 , characterized in that the first spur gearing (5) of the primary spur gear (3) meshes with the first spur gearing (5) of the secondary spur gear (4) in selected operating states and is out of engagement in selected operating states. Rotary slide (1) forward Claim 1 or 2 , characterized in that the second spur toothing (6) of the primary spur gear (3) meshes with the second spur toothing (6) of the secondary spur gear (4) and is out of engagement in selected operating states. Rotary valve (1) according to one of the Claims 1 until 3 , characterized in that the rotary slide valve (1) is designed as a 5/4 valve or 4/2 valve. Rotary valve (1) according to one of the Claims 1 until 4 , characterized in that the primary spur gear (3) is designed as a 5/4 rotary slide valve. Rotary valve (1) according to one of the Claims 1 until 5 , characterized in that the secondary spur gear (4) is designed as a 4/2 rotary slide valve. Rotary valve (1) according to one of the Claims 1 until 6 , characterized in that the two switching positions are locked to the secondary spur gear (4) or forming the rotary slide valve via a detent (7) on a valve housing (10). Rotary slide (1) forward Claim 7 , characterized in that the detent (7) is designed such that the meshing teeth are disengaged when locked.

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