DE102016218186A1 - Vane pump, pump system, automatic transmission and motor vehicle - Google Patents

Abstract

The invention relates to a vane - cell pump (5) comprising a stator (6), a rotor (7), a plurality of vanes (8), a first pressure input (9), a second pressure input (10), a first pressure output (11) second pressure outlet (12), and an adjusting mechanism (13). The wings (8) are retractable from the rotor (7) and extendable from the rotor (7) and through the stator (6) and the rotor (7) are a first conveying region (25) with a first displacement volume (V1) and a second delivery region (26) formed with a second displacement volume (V2). Furthermore, the first delivery area (25) and the second delivery area (26) are separated from each other by the rotor (7), wherein the first pressure input (9) and the first pressure outlet (11) are connected to the first delivery area (25). Furthermore, the second pressure input (10) and the second pressure outlet (12) are connected to the second delivery region (26) and the rotor (7) is stationary. In addition, the adjusting mechanism (13) is adapted to displace the stator (6) relative to the fixed rotor (7), whereby the first displacement volume (V1) and the second displacement volume (V2) change, the sum of the first displacement volume (V1) and the second displacement volume (V2) remains constant.

Description

The invention relates to a vane pump. Further claims are directed to a pump system with the vane pump, to an automatic transmission with the vane pump or the pump system and to a motor vehicle with the automatic transmission.

A vane pump typically includes a stator within which an eccentrically mounted rotor is rotatable relative to the stator. The rotor can be driven in rotation in particular by an electric motor, and comprises a plurality of circumferentially distributed, mostly radially extending slots in which wings are arranged radially displaceable. When the rotor rotates, the vanes are pressed radially outwards by the centrifugal forces that arise and contact an inner wall of the stator, which makes it possible to suck in and displace liquid.

From the prior art single-flow, adjustable vane pumps are known. An advantage of such vane pumps is that a flow rate generated by the vane pump can be adjusted exactly to a total demand of a hydraulic system. The disadvantage, however, is that only one pressure level is generated. The entire volume flow is conveyed in a circle. Even if the sequential system has two circuits with different pressure levels (high and low pressure circuit), the total quantity must be brought to the highest pressure level. The part of the volume flow for the low pressure circuit is relaxed to the lower pressure level, which means an energy loss. This leads to a high pump intake capacity or a poor efficiency in a design to a maximum transmission dynamics. Such vane pumps are therefore not strategically capable.

Furthermore, a two-circuit system with strategically capable flow rates and pressure levels in a primary circuit and in a secondary circuit is known. An advantage of such a two-circuit system is that the pump intake capacity can be reduced by a lower pressure level and a divisible volume flow.

Hydraulic systems with two circuits usually differ in the requirements of the respective circuits. Often there is a high pressure circuit and a low pressure circuit, which in turn - depending on the operating condition - have different volume flow requirements. If such systems are operated with a constant pump with a pressure circuit, the fluid must be raised to the high pressure and the supply of the low circuit of this pressure (= energy) is destroyed.

The DE 10 2004 025 764 A1 shows a hydraulic system with two pressure circuits, in which there are different pressures and a double-stroke vane pump, both pumping areas each supply a pressure circuit. If the two pressure circuits differ in their volumetric flow requirement, the double-stroke vane pump can also be designed asymmetrically. Depending on the operating state, it is possible that the respective volume flow demand of the pressure circuits changes, whereupon the disclosed double-stroke vane pump can not react disadvantageously due to the rigid distribution of their displacement volumes.

An object of the present invention may therefore be to provide a double-stroke vane pump or a pump system, by means of which a pressure and a delivery volume flow in a high-pressure circuit and in a low-pressure circuit can be adjusted separately as needed.

The object is solved by the subject matters of the independent claims. Advantageous embodiments are subject of the dependent claims, the following description and the figures.

According to a first aspect of the invention, there is provided a vane pump including a stator, a rotor, a plurality of vanes, a first pressure input, a second pressure input, a first pressure output, a second pressure output, and an adjustment mechanism.

The wings are retractable into the rotor and extendable out of the rotor. In particular, the wings can be mounted in a known manner in radial slots of the rotor, so that they move radially outward by a centrifugal force during rotation of the rotor until they touch an inner wall of the stator and so the stroke of the wings during the rotation of the rotor from the inner Contour of the stator is determined.

By the stator and the rotor, a first delivery region with a first displacement volume and a second delivery region with a second displacement volume are formed, wherein the first delivery region and the second delivery region are separated from each other by the stationary rotor. The rotor is arranged within the stator, can rotate, but do not perform translational movements, ie the rotor is stationary. Due to the design of the first delivery region and of the second delivery region, the vane-cell pump according to the invention is one Double-stroke vane pump, since each wing reaches its radially outermost two times and twice its radially innermost position in one revolution of the rotor, ie performs two strokes. In this case, the stator and the rotor for forming the first conveying region and the second conveying region on a suitable and mutually corresponding shape, so that the rotor abuts against opposite inner wall sections of the stator or adjacent at a small distance to the opposite inner wall sections, so that the rotor itself can rotate with the least possible friction losses and very little hydraulic fluid can get from the first delivery area in the second delivery area and vice versa.

Between the rotor, the stator and two adjacent blades a working space is formed in each case whose volume changes due to the lifting movement of the wings, or the changing radial distance between an outer contour of the rotor and an inner contour of the stator. The difference between the maximum and minimum volume of the working space is referred to as the displacement volume, since exactly this volume is conveyed in the respective delivery area from the respective pressure input to the respective pressure outlet. The difference between the maximum and minimum clearance of the inner contour of the stator over the circumference of the stator from the outer contour of the rotor is equal to the maximum lift of a blade when passing through the delivery region and is incorporated proportionally into the calculation of the displacement volume, i. If the distance from the rotor to the stator changes, the displacement volume of the delivery area also changes.

The first pressure input and the first pressure output are connected to the first delivery region, and the second pressure input and the second pressure output are connected to the second delivery region. The adjusting mechanism is further adapted to adjust the stator relative to the stationary rotor. By adjusting the relative position of the stator to the rotor, the size of the first displacement volume and the size of the second displacement volume changes such that a reduction of the first displacement volume leads to an increase of the second displacement volume and vice versa. This variation possibility of the displacement volumes can influence a respective volume flow, which is conveyed via the first pressure outlet and via the second pressure outlet, for example in a high-pressure circuit and in a low-pressure circuit.

The vane pump according to the invention thus represents a double-stroke vane pump with two floods, wherein a first flood is passed over the first pressure input, the first delivery region and the first pressure output, and a second tide is passed over the second pressure input, the second delivery region and the second pressure output , The two floods do not feed one and the same pressure circuit, but are led separately from the vane pump. As a result, the pressure and the volume flow in the respective pressure circuit, which is connected to the first pressure outlet or to the second pressure outlet, can be set separately from one another. A core of the invention is therefore to provide an adjustable stator or cam ring, by means of whose variable relative position to the rotor of the vane pump, a delivery volume in a primary pressure circuit (in particular a high pressure circuit) or in a secondary pressure circuit (in particular a low pressure circuit) can be adjusted. The total delivery volume of the double-stroke vane pump, which results from a sum of a possible delivery volume of the first delivery region and the second delivery region, remains constant. If, in other words, the delivery volume is reduced, which is conveyed via the first pressure outlet, a delivery volume which is conveyed via the second pressure outlet increases, and vice versa.

The volumetric flows delivered by the vane pump can thus be adjusted by means of the above-described variation of the displacement volumes to a demand which exists in the pressure circuits connected to the first pressure outlet and the second pressure outlet. In this way, the volume flow and the pressure within the pressure circuits can be varied with a single vane pump, whereby the vane pump can be operated with a particularly high efficiency.

Preferably, the two conveyor regions are arranged to each other, that in an adjustment of the stator relative to the rotor, the increase or decrease of the maximum distance from the inner contour of the stator to the outer contour of the rotor corresponds to the displacement of the stator, so that the displacement volumes of Change two delivery areas such that the amount of increase in the displacement volume of the one conveying area corresponds to the amount of reduction of the displacement volume of the other conveying area. As a result, the sum of the first displacement volume and the second displacement volume remains constant. This is the case, for example, when the two conveyor areas are rotated by 180 ° relative to one another.

According to a further embodiment, the vane pump further comprises a return element, which the adjusting mechanism counteracts. The return element may comprise, for example, a return spring in a particularly simple form. By means of the return element, the stator can be biased relative to the rotor in a predetermined position, in particular in a position in which the first displacement volume or the second displacement volume is maximum.

The vane pump can also be driven by an internal combustion engine of a motor vehicle. This eliminates the need for a separate drive for the vane pump, which space, components and manufacturing costs can be saved.

Alternatively or additionally, the vane pump can also be driven by an electric motor. As a result, the vane pump can be operated particularly independently and redundantly.

According to a further embodiment, the adjusting mechanism comprises an actuator with a valve. The adjustment mechanism may alternatively comprise an electric actuator. Also alternatively, the adjustment mechanism may comprise a hydraulically actuated actuator. Such adjustment mechanisms are particularly suitable for the adjustment of the stator relative to the rotor of the vane pump.

According to a second aspect of the invention, there is provided a pump system comprising a vane pump according to the first aspect of the invention, and further comprising a pressure regulating valve, a system pressure valve and a pressure limiting valve. The first pressure output of the vane pump is connected to the pressure control valve, the system pressure valve and the pressure relief valve. Furthermore, the pressure regulating valve is adapted to set a system pressure within a high pressure circuit, which is connected to the first pressure output of the vane pump. Further, the system pressure valve is configured to adjust the stator of the vane pump relative to the fixed rotor of the vane pump depending on the system pressure, and the pressure relief valve is adapted to a supernatant present in a low pressure circuit connected to the second pressure output of the vane pump Return hydraulic fluid to the first pressure input of the vane pump.

In a conventional variable fluid pump, a total pump delivery rate is increased to a pressure level within the high pressure circuit, thereby losing energy as the fluid is reduced to the pressure level of the low pressure circuit. In the case of the pump system according to the second aspect of the invention, however, only the required amount can always be made available to the high-pressure circuit (optionally plus a reserve). An excess, which arises in the low-pressure rice, it must be raised only to the pressure level of the low-pressure rice, which compared to the conventional variable displacement energy can be saved.

Furthermore, an automatic transmission may comprise an above-described pump system according to the invention or a vane pump according to the invention described above. Furthermore, a motor vehicle may comprise an automatic transmission with a pump system according to the invention described above.

Embodiments of the invention are explained in more detail below with reference to the schematic drawing. This shows

1 a side view of a vehicle with an embodiment of a transmission according to the invention, which includes an embodiment of an inventive pump system,

2 a sectional front view of an embodiment of a double-stroke vane pump according to the invention for use in the pump system according to 1 wherein a stator of the vane pump is in a first relative position with respect to a rotor of the vane pump,

3 the vane pump after 2 with the stator in a second relative position with respect to the rotor,

4 the vane pump after 2 , wherein the stator is in a third relative position with respect to the rotor, and

5 a hydraulic circuit diagram of an embodiment of a pump system according to the invention for use in the transmission according to 1 ,

That through 1 shown motor vehicle 1 includes a drive in the form of an internal combustion engine 2 for driving the motor vehicle 1 , which with an automatic transmission 3 , connected is. The automatic transmission 3 shows an embodiment of a pump system according to the invention 4 for pressure supply of the automatic transmission 3 with hydraulic oil on. Like the pump system 4 can be equipped, is exemplified by 5 shown.

2 shows a double-stroke vane pump 5 , which is set up in the pump system 4 according to 1 and 5 to be used. The vane pump 5 includes a stator 6 , one inside the stator 6 arranged rotor 7 , a total of eight in the circumferential direction of the rotor 7 distributed wings 8th , a first pressure input 9 , a second pressure input 10 , a first pressure outlet 11 , a second pressure outlet 12 as well as an adjustment mechanism 13 , Of the total of eight wings 8th is for clarity only a wing with a reference numeral (" 8th ") Mistake.

An intended direction of rotation of the rotor 7 about a rotation axis M of the rotor 7 is by a rotary arrow 40 illustrates and proceeds according to the view 2 counterclockwise. The first pressure input 9 is via a first connection line 15 connected to a tank T for hydraulic fluid. Also over the first connection line 15 is the 1 , pressure input 9 with the second pressure input 10 connected. The first pressure output 11 is about one 2 , connecting line 16 with a high pressure circuit not shown 17 connected. The second pressure output 12 is via a third connection line 18 with a low-pressure circuit, not shown 19 connected.

The rotor 7 can in particular by an electric motor (not shown) or the internal combustion engine 2 according to 1 are driven. The eight wings 8th of the rotor are arranged radially displaceably in a plurality of circumferentially distributed and radially extending slots (not shown). During a rotation of the rotor 7 around the center of the rotor 7 become the wings 8th pressed by the resulting centrifugal forces radially outwards and touch an inner wall 20 of the stator 6 , whereby a suction and displacement of hydraulic fluid is made possible.

The rotor 7 has a circular cross section with an outer circumference U and a radius r. The cross section or the inner wall 20 of the stator 6 includes a first straight section 21 , a first arcuate section 22 , a second straight section 23 and a second arcuate portion 24 , The straight sections 21 and 23 have the same length, parallel to each other and are each through the arcuate sections 22 and 24 connected with each other. A distance between the straight sections 21 and 23 is only slightly larger than the radius r of the rotor 7 , This creates a small gap between the inner wall 20 of the stator 6 and the outer circumference U of the rotor 7 which allows the rotor 7 inside the stator 6 rotate and a first conveyor area 25 and a second conveyor area 26 can train. The gap between the stator 6 and the rotor 7 is so small that leaks from the first delivery area 25 in the second funding area 26 and vice versa are negligibly small.

In the by 2 As shown, the rotor rotates 7 counterclockwise and sucks on the one hand a first volume flow Q ₁ hydraulic fluid at a first pressure p ₁ from the tank T via the first connecting line 15 and the first pressure input 9 in the in 2 left illustrated first conveyor area 25 at. Through the wings 8th of the rotor 7 is the first volume flow Q ₁ hydraulic fluid at a second pressure p ₂ from the first delivery area 25 over the first pressure outlet 11 out into the second connection line 16 and about it in the high-pressure circuit 17 promoted. On the other hand, the rotor sucks 7 a second volume flow Q ₂ hydraulic fluid at a third pressure p ₃ from the tank T via the first connecting line 15 and the second pressure input 10 in the in 2 right illustrated second conveyor area 26 at. Through the wings 8th of the rotor 7 is the second volume flow Q ₂ hydraulic fluid at a fourth pressure p ₄ from the second delivery area 26 via the second pressure outlet 12 out into the third connection line 18 and above in the low-pressure rice 19 promoted.

In the by 2 The example shown is the rotor 7 in a middle position within the stator 6 , In this middle position is the rotor 7 to the two arcuate sections 22 and 24 of the cross section of the stator 6 equidistant. As a result, a first lifting or displacement volume V _{1 of} the first conveying region 25 equal to a second displacement volume V _{2 of} the second delivery area. Consequently, the first volume flow Q ₁ hydraulic fluid is equal to the second volume flow Q ₂ hydraulic fluid. In other words, there are the rotor 7 under the stator 6 in a middle relative position to each other, which allows for the two pressure chambers 25 and 26 equal volume flows Q ₁ and Q ₂ hydraulic fluid into the high-pressure circuit 17 and in the low-pressure circuit 19 can be promoted.

The relative position between the stator 6 and the rotor 7 can by means of the adjustment mechanism ' 13 to be changed. The adjustment mechanism 13 is in the area of through 2 left illustrated first arcuate portion 22 of the stator 6 arranged. In the by 2 embodiment shown comprises the adjustment mechanism 13 a hydraulically actuated actuator with a stationary cylinder element 27 and one within the cylinder member 27 linearly displaceable piston 28 with a piston rod 29 , The piston rod 29 is so with an outer wall 30 of the stator 6 in the region of its first arcuate section 22 coupled to that of the stator 6 linear to the right is moved when the piston rod 29 from the cylinder element 27 is extended. Furthermore, the piston rod 29 so with the outer wall 30 of the stator 6 in the region of its first arcuate section 22 coupled to that of the stator 6 is moved to the left when the piston rod 29 in the cylinder element 27 is retracted. The straight sections 21 and 23 the inner wall 20 of the stator 6 and one to the straight sections 21 and 23 parallel inner wall 31 of the cylinder element 27 serve as a linear guide for the stator 6 along the outer circumference U of the rotor 7 , In particular, a stroke of the piston rod extends 29 parallel to the straight sections 21 and 23 the inner wall 20 of the stator 6 and the piston rod is with the stator 6 in a region of a vertex of the first arcuate portion 22 the inner wall 20 of the stator 6 connected.

The above-described linear displacement of the stator 6 by means of the piston rod 29 the adjustment mechanism 13 acts a spring force of a first spring 32 contrary, in the area of 2 right illustrated second arcuate portion 24 of the stator 6 is arranged and according to the outer wall 30 of the stator 6 in the region of the second arcuate section 24 acts. The feather 32 is on a housing wall 33 the vane pump 5 or the pump system 4 firmly mounted. The housing wall 33 serves as an abutment. In particular, the spring force of the first spring 32 parallel to the straight sections 21 and 23 the inner wall 20 of the stator 6 oriented and the first spring 32 is with the stator 6 in an area of a vertex of the second arcuate portion 24 the inner wall 20 of the stator 6 connected.

3 shows the vane pump 5 to 2 , where the stator 6 in a second relative position ("maximum delivery low pressure circuit") relative to the rotor 7 located. The adjustment mechanism 13 has by means of its piston rod 29 the stator 6 opposite the stationary rotor 7 shifted to the left, that the first displacement volume V _{1 of} the first conveying area 25 has been reduced and the second displacement volume V _{2 of} the second conveying area 26 has been increased (V ₁ <V ₂ ). In this case, the second displacement volume V _{2 has} increased by the amount by which the first displacement volume V _{1 has been} reduced. A total displacement volume V _ges , which is composed of the first displacement volume V ₁ and the second displacement volume V ₂ , has therefore remained constant (V _ges = V ₁ + V ₂ = const.). Corresponding to the changed volumes V ₁ and V ₂ , the volume flows Q ₁ and Q _{2 also change} , so that over the first delivery range 25 correspondingly less hydraulic fluid is conveyed than over the second delivery area 26 (Q ₁ <Q ₂ ). In this second relative position is the in the low pressure circuit 19 delivered volume flow Q ₂ maximum and that in the high pressure circuit 17 delivered volume flow Q ₁ is minimal.

4 shows the vane pump 5 to 2 , where the stator 6 in a third relative position ("maximum flow rate high pressure circuit") relative to the rotor 7 located. The adjustment mechanism 13 has by means of its piston rod 29 the stator 6 opposite the stationary rotor 7 shifted to the right, that the second displacement volume V _{2 of} the second conveying area 26 has been reduced and the first displacement volume V _{1 of} the first conveying area 25 has been increased (V ₁ > V ₂ ). In this case, the first displacement volume V _{1 has} increased by the amount by which the second displacement volume V _{2 has been} reduced. The total displacement volume V _ges , which is composed of the first displacement volume V ₁ and the second displacement volume V ₂ , has again remained constant (V _ges = V ₁ + V ₂ = const.). Corresponding to the changed volumes V ₁ and V ₂ , the volume flows Q ₁ and Q _{2 also change} , so that over the second delivery range 26 correspondingly less hydraulic fluid is conveyed than over the first delivery area 25 (Q ₁ > Q ₂ ). In this second relative position is the in the high pressure circuit 17 delivered volume flow Q ₁ maximum and that in the low pressure circuit 19 delivered volume flow Q ₂ is minimal. The stator 6 is through the spring 32 in the through 4 shown relative position with respect to the rotor 7 biased, the stator 6 from this relative position by means of the piston rod 29 the adjustment mechanism 13 especially in the 2 and 3 shown relative positions can be moved linearly. Apart from the relative positions, which by 2 to 4 can be shown, the stator 6 in any number of other relative positions relative to the rotor 7 be moved, with these other relative positions in particular between by 3 and 4 can be shown relative positions.

5 shows a pump system 4 , which is next to a vane pump 5 a pressure regulating valve or a pressure regulator 34 in the form of a 3/2-way valve with any number of intermediate switching positions, a system pressure valve 35 in the form of a 4/2-way valve with any number of intermediate positions and a pressure relief valve 36 includes. The arbitrarily many intermediate switching positions of a control valve are hereinafter also referred to as control positions. At the vane pump 5 it may in particular be a vane pump, as by 2 to 4 is shown.

The first pressure input 9 the vane pump 5 is via a first connection line 15 and a filter F with a tank T for the Operating medium, in particular hydraulic fluid connected. Also over the first connection line 15 is the first print input 9 with a second pressure input 10 the vane pump 5 connected. The first pressure output 11 is via a second connection line 16 with a high pressure circuit shown schematically simplified 17 connected. The second pressure output 12 is via a third connection line 18 with a low-pressure circuit shown schematically simplified 19 connected.

The pressure regulator 34 has an input-side connection 37 , a tank-side connection 38 and an output side port 39 on. Here is the input side connection 37 with the second connection line 16 , the tank side connection 38 is with the unpressurized tank T, and the output side connection 39 is with a first control line 42 connected.

The pressure regulator 34 is between a first switching position, which by 5 is shown, and a second switching position adjustable in any number of control positions. The pressure regulator 34 is by a spring force of a second spring 40 biased in the first switching position when a proportional solenoid 41 is de-energized. By means of the proportional magnet 41 can the pressure regulator 34 be brought from the first switching position against the spring force in the second switching position or in one of the control positions, so that virtually infinitely a pressure in the connecting line 16 can be set.

Inside the pressure regulator 34 is in its first switching position of the first input-side connection 37 shut off and the second input side connection 38 is with the output side connection 39 connected. In the second switching position of the pressure regulator 34 is the first input-side connection 37 with the output side connection 39 connected, and the second input side connection 38 is locked.

The one in the first control line 42 prevailing pressure can be over a first branch 43 on the pressure regulator 34 act, so that a corresponding pressure force of the hydraulic fluid within the first branch 43 in the same direction as the spring force of the second spring 40 can work.

The system pressure valve 35 has a first input side port 44 , a second input side terminal 45 , a first output side port 46 and a second output side terminal 47 on.

The system pressure valve 35 is between a first switching position, which by 5 is shown, and a second switching position controllable, or can assume arbitrary control positions in between.

The system pressure valve 35 is by a spring force of a third spring 48 biased in the first switching position when a fifth control line 55 is depressurized. The first control line 42 , which with the output side connection 39 of the pressure regulator 34 is connected, has a second branch 49 on. The one in the first control line 42 prevailing pressure can be over the second branch 49 on the system pressure valve 35 act, so that a corresponding pressure force of the hydraulic fluid within the second branch 49 in the same direction as the spring force of the third spring 48 can work. This is the system pressure valve 35 from the pressure regulator 34 through the second branch 49 pilot operated and can control the pressure in the system by adjusting the vane pump 5 in the high pressure circuit 17 subsidized volume flow, hereinafter also referred to as flow rate, regulate.

Within the system pressure valve 35 is in its first switching position, which represents the initial position, the first input-side terminal 44 with the first output side connection 46 connected, and the second input side connection 45 is with the second output side connection 47 connected. In a control position or the second switching position of the system pressure valve 35 is the first input-side connection 44 with the second output side connection 47 connected, and the second input side connection 45 is with the first output side connection 46 connected.

The connection side is the first input side connection 44 with a second control line 50 connected, the second input-side connection 45 is with a third control line 51 connected, the first output side connection 46 is connected to the tank T, and the second output side terminal 47 is with the second connection line 16 connected.

The pressure relief valve 36 has an input-side connection 52 and an output side port 53 on. The input side connection 52 is with the third connection line 18 connected. The output side connection 53 is with the first connection line 15 connected.

The in the second control line 50 prevailing pressure can be so on the stator 6 the vane pump 5 act that the stator 6 against the spring force of the first spring 32 its relative position to the rotor 7 changed, much like this 2 to 4 is described. In the by 5 As shown, the pressure acts within the second control line 50 at a position P ₂ on the stator 6 in the region of its first arcuate section 22 , The point P ₂ is in the region of a vertex of the first arcuate portion 22 ,

The in the third control line 51 prevailing pressure can be so on the stator 6 the vane pump 5 act that the stator 6 in the direction of the spring force of the first spring 32 its relative position to the rotor 7 changed, much like this 2 to 4 is described. In the by 5 As shown, the pressure acts within the third control line 51 at a position P ₁ on the stator 6 in the region of the second arcuate portion 24 , The point P ₁ lies in the region of a vertex of the first arcuate portion 22 , At the point P _{1 also} engages the spring force of the first spring 32 in the same direction as the pressure force of the hydraulic fluid within the third control line 51 ,

At a system start, the stator is located 6 the vane pump 5 due to the spring force of the first spring 32 in a second relative position ("maximum flow rate high pressure circuit") to the rotor 7 the vane pump 5 , In this second relative position is the in the high pressure circuit 17 delivered volume flow Q ₁ maximum and that in the low pressure circuit 19 delivered volume flow Q ₂ is minimal, similar to that related to 4 is described.

The pressure regulator 34 is in its first switching position, in which the in the second connecting line 16 prevailing second pressure p _{2 of} the vane pump 5 at the shut off first input side connection 37 the pressure regulator 34 is applied. Furthermore, the first control line 42 through the connection with the tank T depressurized.

Once the over the pressure regulator 34 set pressure within the high pressure circuit 17 and within the second connection line 16 is achieved acts in the second connection line 16 prevailing pressure over a fourth connection line 54 such on the system pressure valve 35 that is the system pressure valve 35 moved to its second switching position, wherein a control edge (not shown) is opened, so that the second connecting line 16 with the second control line 50 is connected and hydraulic fluid via the second control line 50 to point P ₂ can flow. This will be the stator 6 shifted linearly to the right, that of the first conveyor area 25 delivered volume flow hydraulic fluid is reduced, causing in the high pressure circuit 17 , which with the first pressure outlet 11 is connected, also less hydraulic fluid is conveyed. At the same time, the second conveyor area is being used 26 promoted volume flow hydraulic fluid increases, causing in the low-pressure circuit 19 , which with the second pressure outlet 12 is connected, according to more hydraulic fluid is conveyed. Depending on the intended use, the hydraulic fluid may be, for example, a coolant.

The system pressure valve 35 reduced over a closing of the control edge to the point P ₁ and via an opening of the control edge to the point P _2, the flow rate in the high pressure circuit 17 so far until the over the pressure regulator 34 set system pressure through the in the high pressure circuit 17 funded volume can be saturated (pressure offset as security).

By the corresponding enlargement of the delivery volume, which in the low-pressure circuit 19 is promoted, this is an excess amount of hydraulic fluid available, which by that of a main pressure (the pressure which in the second connecting line 16 prevails and over a fifth control line 55 on the pressure relief valve 36 acts) pilot operated pressure relief valve 36 discharged and back to the vane pump 5 is directed. This is a particularly good filling behavior of the vane pump 5 allows, since the excess quantity does not have to be sucked again from the tank T. The pressure relief valve 36 regulates the pressure in the low-pressure circuit 19 (By the pilot control described above) to a fixed ratio between the pressures of the high pressure circuit 17 and the low-pressure circuit 19 ,

If in the high pressure circuit 17 a higher pressure level (= higher volume flow requirement) is required, a pressure regulator pressure by means of the proportional solenoid 41 increases, whereby the control edge to the point P ₁ is opened further and the flow rate in the high pressure circuit 17 until it reaches the intended higher level. In the event of high-pressure drops, eg due to rapid fillings, the control edge is also opened to the point P ₁ because the pressure regulator pressure is the pressure regulator 34 shifts (no more equilibrium condition due to pressure drop). This creates a self-regulating system.

If one assumes, for example, that in the high pressure circuit 17 a volume flow requirement of 5 l / min at a system pressure of 4 bar, and that in the low-pressure circuit 19 a volumetric flow requirement of 10 l / min at a system pressure of 1 bar, there is a hydraulic power (volume flow requirement multiplied by system pressure) of the vane pump 5 of 34 W for the high pressure circuit 17 and 17 W for the low-pressure rice 19 , In comparison, a conventional variable in the high pressure circuit 17 and in the low-pressure circuit 19 promote a total flow of 15 l / min at a system pressure of 4 bar, resulting in a hydraulic pump power of 100W. It follows that the vane pump 5 An approximate 50% savings in hydraulic power compared to a conventional variable displacement pump.

LIST OF REFERENCE NUMBERS

1

motor vehicle

2

Internal combustion engine

3

automatic transmission

4

pump system

5

Vane pump

6

stator

7

rotor

8th

wing

9

first pressure input

10

second pressure input

11

first pressure outlet

12

second pressure output

13

adjustment

14

Direction of rotation rotor

15

first connection line

16

second connection line

17

High pressure circuit

18

third connection line

19

Low pressure rice

20

Inner wall stator

21

first straight section

22

first arcuate section

23

second straight section

24

second arcuate section

25

first funding area

26

second funding area

27

cylindrical member

28

piston

29

piston rod

30

Outer wall stator

31

Inner wall Cylinder element

32

first spring

33

housing wall

34

Pressure regulator or pressure control valve

35

System pressure valve

36

Pressure relief valve

37

input side connection pressure regulator

38

tank-side connection pressure regulator

39

Output side pressure regulator

40

second spring

41

proportional solenoid

42

first control line

43

first branch first control line

44

first input side connection system pressure valve

45

second input side connection system pressure valve

46

first output connection system pressure valve

47

second output connection system pressure valve

48

third spring

49

second branch first control line

50

second control line

51

third control line

52

Input side connection Pressure relief valve

53

Output side connection Pressure relief valve

54

fourth control line

55

fifth control line

T

tank

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• DE 102004025764 A1 [0006]

Claims (12)

Vane pump ( 5 ), comprising - a stator ( 6 ), - a rotor ( 7 ), - several wings ( 8th ), - a first pressure input ( 9 ), - a second pressure input ( 10 ), - a first pressure outlet ( 11 ), - a second pressure outlet ( 12 ), where - the wings ( 8th ) in the rotor ( 7 ) are retractable and from the rotor ( 7 ) are extendable, - by the stator ( 6 ) and the rotor ( 7 ) a first funding area ( 25 ) with a first displacement volume (V ₁ ) and a second delivery area ( 26 ) are formed with a second displacement volume (V ₂ ), - the first conveying region ( 25 ) and the second funding area ( 26 ) from each other through the rotor ( 7 ), - the first pressure input ( 9 ) and the first pressure outlet ( 11 ) with the first funding area ( 25 ), - the second pressure input ( 10 ) and the second pressure outlet ( 12 ) with the second funding area ( 26 ), - the rotor ( 7 ) is stationary, characterized in that the vane pump has an adjusting mechanism ( 13 ), which is adapted to the stator ( 6 ) relative to the stationary rotor ( 7 ), whereby the first displacement volume (V ₁ ) and the second displacement volume (V ₂ ) change. Vane pump ( 5 ) according to claim 1, characterized in that the two conveying regions are arranged relative to one another such that during an adjustment of the stator ( 6 ) relative to the rotor ( 7 ) the increase or decrease of the maximum distance from an inner contour of the stator ( 6 ) to an outer contour of the rotor ( 7 ) the adjustment of the stator ( 6 ), so that the displacement volumes (V ₁ , V ₂ ) of the two conveyor areas ( 25 . 26 ) such that the amount of increase in the displacement volume (V ₁ ) of the one conveying region ( 25 ) the amount of reduction of the displacement volume (V ₂ ) of the other production area ( 26 ), whereby the sum of the first displacement volume (V ₁ ) and the second displacement volume (V ₂ ) remains constant. Vane pump ( 5 ) according to claim 2, characterized in that the two conveyor areas ( 25 . 26 ) are arranged to each other so that they are rotated by 180 ° to each other. Vane pump ( 5 ) according to one of claims 1 to 3, the vane pump ( 5 ) further comprising a return element ( 32 ), which the adjusting mechanism ( 13 ) counteracts. Vane pump ( 5 ) according to one of the preceding claims, characterized in that the vane pump ( 5 ) via an internal combustion engine ( 2 ) of a motor vehicle ( 1 ) can be driven. Vane pump ( 5 ) according to one of the preceding claims, wherein the vane pump ( 5 ) can be driven by an electric motor. Vane pump ( 5 ) according to any one of the preceding claims, wherein the adjusting mechanism ( 13 ) an actuator with a valve ( 35 ). Vane pump ( 5 ) according to any one of the preceding claims, wherein the adjusting mechanism ( 13 ) comprises an electric actuator. Vane pump ( 5 ) according to any one of the preceding claims, wherein the adjusting mechanism ( 13 ) a hydraulically actuable actuator ( 27 to 29 ). Pump system ( 4 ) comprising: - a vane pump ( 5 ) according to one of the preceding claims, - a pressure regulating valve ( 34 ), - a system pressure valve ( 35 ) and - a pressure relief valve ( 36 ), where - the first pressure outlet ( 11 ) of the vane pump ( 5 ) with the pressure control valve ( 34 ), the system pressure valve ( 35 ) and the pressure relief valve ( 36 ), - the pressure regulating valve ( 34 ) is adapted to a system pressure within a high pressure circuit ( 17 ), which is connected to the first pressure outlet ( 11 ) of the vane pump ( 5 ) connected. - The system pressure valve ( 35 ) is adapted to, depending on the system pressure, the stator ( 6 ) of the vane pump ( 5 ) relative to the stationary rotor ( 7 ) of the vane pump ( 5 ), and - the pressure relief valve ( 36 ) is set up, one in a low-pressure rice ( 19 ), which with the second pressure outlet ( 12 ) of the vane pump ( 5 ), existing excess hydraulic fluid to the first pressure input ( 9 ) of the vane pump ( 5 ). Automatic transmission ( 3 ) comprising a pump system ( 4 ) according to claim 10 or a vane pump ( 5 ) according to one of claims 1 to 9. Motor vehicle ( 1 ) comprising an automatic transmission ( 3 ) according to claim 11.

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