The invention relates to displacement pumps, in particular internal-axle gear pumps, but also wing cell pumps or for example also pendulum slider pumps, whose volume flow can be varied according to requirement, i.e. can be adjusted. The pumps in accordance with the invention are preferably used as lubricant oil pumps for internal combustion engines, wherein the internal combustion engine itself preferably drives the lubricant oil pump in question. The internal combustion engine can in particular be a drive motor, preferably a piston motor, of a vehicle. The specific volume flow, i.e. the volume flow delivered per revolution of a delivery wheel of the pump, can preferably be adjusted continuously. The displacement pumps can also be advantageously used as supply pumps for automatic transmissions in vehicles and when used in this way are also preferably driven by the drive motor of the vehicle in question. Although the displacement pump of the invention, which can be adjusted according to requirement, is suitable in particular for such applications, in which with increasing drive speed, the fluid requirement increasingly falls short of the delivery volume of pumps whose specific delivery volume is constant, a pump in accordance with the invention can also be advantageously employed in other situations, in which for example the drive speed of the pump is constant and the fluid requirement of the aggregate to be supplied fluctuates for other reasons.
Displacement pumps formed as gear ring pumps, such as the invention also relates to in particular, are known from DE 297 03 369 U1 and EP 0 846 861 B1 which is based on it.
In the known variable pumps, the external rotor of the gear ring running set is rotatably mounted in a variable ring which surrounds the external rotor and rolls off without slipping in the pump casing via an internal-external toothing, such that in accordance with these kinematic ratios, the eccentric axis of the gear ring running set rotates by up to 90° relative to the casing during the varying process. This enables a delivery amount to be varied from a maximum to almost zero, with as small an adjusting path as possible.
However, it has proven in practice that the design space available in increasingly compact reciprocating piston motors is becoming smaller and smaller. Since these pumps are preferably arranged in the oil sump of the crankcases and since a mass-balance shaft often also has to be additionally accommodated in this region, together with other influencing factors such as conductor frame fortification of the crankcase and a highly pitched oil pan for ground clearance and the arrangement of the vehicle steering parts, the outer diameter of the variable pump is too large. Since, due to the heated idling at low motor speed, the pump has to exhibit a specific minimum delivery amount, the diameter of the gear ring running set cannot be arbitrarily reduced. Limits are also set on enlarging the running set width, for reasons of space and due to the suction limits of the teeth. Wide running sets have the additional disadvantage that during speed regulation, the overthrust losses between the converging and diverging teeth cells caused by differential varying are very high.
It is therefore an object of the invention to provide a displacement pump which exhibits smaller dimensions, with respect to both the diameter and width of the running set, for the same specific delivery amount.
The displacement pump with variable volume flow in accordance with the invention comprises a casing and a chamber which is formed in the casing and comprises an inlet opening on a low pressure side and an outlet opening on a high pressure side for a fluid. The pump can for example be an internal gear pump, a wing cell pump or a pendulum slider pump. The pump further comprises an internal rotor which is accommodated in the chamber and can be rotated about a rotational axis, and a ring which is accommodated in the chamber and has a central ring axis which surrounds the internal rotor. In the case of rotary driving at least one of the internal rotor and the ring, the ring and the internal rotor form at least one delivery cell in which the fluid is delivered from the low pressure side to the high pressure side. An adjusting device is arranged such that during an adjusting movement, it rolls off on the casing without slipping. In accordance with the invention, the internal rotor is fixed to the adjusting device such that it can be rotated about the rotational axis. Furthermore, the position of the rotational axis relative to the ring axis of the ring can be adjusted by the adjusting movement of the adjusting device.
By adjusting the internal rotor relative to the casing and the surrounding ring in order to adjust the specific volume flow, sealing the delivery space formed between the internal rotor and the outer ring can be simplified.
If the pump is a gear ring pump, then the outer ring forms an external rotor. In such embodiments, driving the gear ring running set formed by the internal rotor and the external rotor via the external rotor is facilitated. As compared to rotary driving via the internal rotor, the pump speed in the case of rotary driving via the external rotor is advantageously increased in accordance with the ratio of the numbers of teeth of the internal rotor and the external rotor, hence the diameter of the pump can be reduced. The outer ring is also a rotor in a pendulum slider pump, such as is for example described in FR 980766. In a wing cell pump, the outer ring can be fixed relative to the casing, or the casing itself can form the internal cylindrical surface for a wing wheel forming the internal rotor.
It is advantageous if an adjusting device which adjusts the specific volume flow does not surround the internal rotor and the outer ring but is arranged axially adjacent to them. It is particularly advantageous if arranging the adjusting device adjacent to the internal rotor and/or the outer ring is combined with adjusting the specific volume flow by adjusting the internal rotor. The adjusting device preferably rotationally mounts the internal rotor such that it slaves the internal rotor during its own adjusting movement by being fixedly connected to the internal rotor with respect to the adjusting movement. The adjusting device can for example comprise a toothing which is in toothed engagement with a toothing of the casing during an adjusting movement. The toothing of the adjusting device is preferably a round-flank toothing. A centre point of a flank circle of a tooth of the toothing of the adjusting device can for example approximately describe a hypocycloid when rolling off on the casing.
By omitting the variable ring around the external rotor and by increasing the speed of the internal rotor in proportion to the numbers of teeth from the external rotor to the internal rotor as compared to the drive speed, the design space of the variable pump required is reduced superproportionally, for the same specific delivery amount.
Such a variable pump in accordance with the invention is thus also suitable for small-volume internal combustion engines, in which particular value is placed on reducing the hydrostatic losses and the circulated amount of oil at high speeds.
The compactness of a variable displacement pump in accordance with the invention can hardly be surpassed. Since the shaft bearings are rid of any hydrostatic load, and are only then loaded by the traction rod of a continuously variable transmission such as is preferably used for driving, the diameter of the shaft can be reduced. The smaller effective running set width also improves the suction capacity and reduces the danger of cavitation. The volumetric efficiency is also improved due to the augmented high-speed running. This is also due to the fact that the pinion engagement between the external rotor and the internal rotor then trails at the point of maximum toothed engagement, such that the pressure side of the toothing is sealed better than the suction side.
In accordance with preferred embodiments, the adjusting device adjusts hydraulically by being charged with a fluid pressure which is fed back from the high pressure side of the pump to the adjusting device. The high pressure side of the pump reaches from the high pressure side of the pump chamber to the point or points of the aggregate or number of aggregates to be supplied, from which the fluid, relieved of pressure, is fed back to a fluid reservoir. It can also be advantageous to tap the fluid pressure of the high pressure side of the pump at a location outside the displacement pump and to charge the adjusting device with the pressure in order to vary the volume flow. The pressure can for example be tapped at a crankshaft main gallery of the motor.
In a preferred embodiment, the fluid pressure acting in the pump chamber on the high pressure side, in combination with the fluid pressure fed back to the adjusting device, generates the adjusting force for adjusting. The adjusting force can for example be formed from at least one of the two hydraulic adjusting forces which act on the adjusting device and/or internal rotor. In particular, the adjusting device can be adjusted by an adjusting force against the force of an elastic component. The two adjusting forces are advantageously superimposed positively on each other, preferably by generating adjusting moments in the same direction. In this way, it is possible to achieve a varying which reacts particularly sensitively to changes in pressure. The invention thus also relates to a displacement pump with variable volume flow, comprising the features of the preamble of at least one of the independent claims in combination with feeding the fluid pressure back to the adjusting device and charging the adjusting device with the fluid pressure fed back, in a direction such that the adjusting force thus generated is superimposed positively on an adjusting force generated by the fluid pressure of the high pressure side of the pump chamber acting on one of the internal rotor and the outer ring, the sum of the two forces being greater than each of the two individual forces.
For the adjustability of the variable pump, such an embodiment gives rise to the advantage that the hydraulic adjusting forces of the internal rotor are added, over its bearing journal on the one hand and those between the adjusting device—preferably formed as an adjusting plate—and the casing, and not subtracted as with the known displacement pump. This advantage is very important, particularly for cold starts in which a quick adjustment to a zero delivery amount is necessary in order to prevent damage to the oil filter and oil conduits. Up until now, it has been necessary here to provide an additional pressure control valve due to the inertia of the adjustment to zero.
Although positively superimposing the two hydraulic adjusting forces is particularly advantageous in its own right alone, this embodiment is preferably combined with adjusting the internal rotor or arranging the adjusting device axially adjacent to the internal rotor and/or the outer ring, and particularly preferably combined with both these features.
Due to the machinability of the internal toothing in the casing for the adjusting transmission, the number of teeth here cannot be selected to be arbitrarily large. A round-flank toothing is most suitable on the adjusting plate, such that the internal toothing in the casing—which preferably comprises one tooth more than the external toothing of the adjusting plate—can be machined using a rotating cutting tool (drill rod), as is known from the known variable pump comprising a variable ring in
No eccentric chucks are required for machining the casing parts, since the shaft and external rotor bearings are concentric. The depth of the internal toothing of the casing is minimised and no longer has to be machined over the entire running set width, as with the known design. This toothing can be high-precision manufactured on a CNC machine with a C axis and path-controlled HSC (high speed cutting) spindle unit in a clamp together with the other machining operations. This results in a considerable reduction in the expenditure of time for machining the toothing of the casing.
The subject of the invention is shown in the drawings by way of the example of a variable internal gear pump, arranged in the oil sump, for a four-cylinder passenger car engine. This does not, however, mean that the invention is restricted to such an application. It could also, for example, be used in an automatic transmission as an oil pressure pump for switching and for supplying the transmission parts with oil. The variable pump would then be positioned at the end of a continuous transmission input shaft, such that in this case, the chain wheel shown in the drawings is omitted, and instead the pump shaft is coupled, concentrically and rotationally fixed, to the transmission input shaft.
Example embodiments of the invention are explained below on the basis of figures. Features disclosed by the example embodiments, each individually and in any combination of features, advantageously develop the subjects of the claims and also the embodiments described above.
Specifically, there is shown:
For explaining the function in the individual figures, the rotational direction of the running set shall be in the indicated direction of the arrow 32, such that the respective suction and pressure side in accordance with the expanding and compressing delivery cells of the teeth is clearly provided. In the cover 30, the suction support 31 is arranged on the suction side of the running set, on which side the variable spring 28 can also be seen. Thus, the spaces of the variable spring 28 and the rolling cylinders 24 and 25, and the sections of the toothing shown on the right of the image in
As the viscosity of the oil increases (e.g. during cold starts) or as the speed of the pump increases, the system pressure in the pressure chamber 35 and in the compressing delivery cells of the gear ring running set increases. A sum of adjusting moments arises around the velocity pole via the radial acting surfaces on the internal rotor 4 and on the adjusting plate 13, such that the variable spring 28 is no longer capable of holding the adjusting plate 13 on the stopper 36. The variable system thus enters a poise which is determined by the moment equilibrium between the sum of the hydraulic adjusting moments and the moment of the variable spring 28 about the velocity pole Ml. As the system pressure in the pressure chamber 35 increases, the adjusting plate 13 rotates clockwise in accordance with the representation in
The position P2, i.e. a rotation by 90° of the centre point DI of the internal rotor 4 in accordance with
As already mentioned in the introductory part of the description, it is expedient for the adjusting plate 13 not to roll off on the reference circles of the toothings between the adjusting plate 13 and the casing 1 but on two cylinder attachments, which roll off on each other, on the adjusting plate and the casing. The embodiment of the cylinder attachment on the adjusting plate is shown somewhat more clearly in
Latterly, attempts have been made to control the delivery amount of the pump in accordance with the oil pressure in front of the crankshaft bearings by providing one or more pressure sensors in the main gallery of the crankshaft which tap the oil pressure there and supply it to the pressure chamber 35 of the adjusting pump. In this case, the pressure chamber 35 would then have to be hydraulically partitioned from the main flow channel of the pressure side of the pump.
Number | Date | Country | Kind |
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20 2004 004 231.2 | Mar 2004 | DE | national |