Axial Piston Compressor, Especially for the Air Conditioning System of a Motor Vehicle
Axial piston compressor, especially a compressor for the air-conditioning system of a motor vehicle, having a housing and, for drawing in and compressing a coolant, a compressor unit arranged in the housing and driven by means of a drive shaft (104), the compressor unit comprising pistons (118), which move axially back and forth in a cylinder block, and a tilt plate (swash plate or wobble plate; or tilt ring (107) which drives the pistons and rotates together with the drive shaft (104). The geometry and dimensioning of all parts moved in translation, such as axial pistons (118), piston rods or sliding blocks (121, 122) or the like, on the one hand, and all parts moved in rotation, such as the tilt plate (107), members for conjoint movement or the like, on the other hand, are such that, for any desired tilt angles (α) of the tilt plate (107), between a predetermined minimum tilt angle (αmin) and a predetermined maximum tilt angle (αmax), the moment Mk,ges due to the masses moved in translation, such as pistons (118), sliding blocks (121, 122), piston rods or the like, is approximately equal to the moment MSW due to the moment of deviation, that is to say the moment due to the mass inertia of the tilt plate (107).
The invention relates to an axial piston compressor, especially to compressors for motor vehicle air-conditioning systems, having a housing and, for drawing in and compressing a coolant, a compressor unit arranged in the housing and driven by means of a drive shaft, the compressor unit comprising pistons, which move axially back and forth in a cylinder block, and a tilt plate (swash ring, tilt ring or wobble plate) which drives the pistons and rotates together with the drive shaft.
An axial piston compressor of such a kind is known, for example, from DE 197 49 727 A1. That compressor comprises a housing in which, in a circular arrangement, a plurality of axial pistons are arranged around a rotating drive shaft. The drive force is transmitted from the drive shaft, by way of a member for conjoint movement, to an annular tilt plate and in turn, from there, to the pistons displaceable in translation parallel to the drive shaft. The annular tilt plate is pivotally mounted on a sleeve which is mounted on the drive shaft so as to be axially displaceable. In the sleeve there is provided an elongate hole, through which the mentioned member for conjoint movement engages. Consequently, the capability of the sleeve for axial movement on the drive shaft is limited by the dimensions of the elongate hole. Assembly is carried out by passing the member for conjoint movement through the elongate hole. The drive shaft, member for conjoint movement, sliding sleeve and tilt plate are arranged in a so-called drive mechanism chamber, in which gaseous working medium of the compressor is present at a particular pressure. The delivery volume and consequently the delivery output of the compressor are dependent on the pressure ratio between the suction side and delivery side of the pistons or correspondingly dependent on the pressures in the cylinders on the one hand and in the drive mechanism chamber on the other hand.
A somewhat different kind of construction of an axial piston compressor is described, for example, in DE 198 39 914 A1. The tilt plate is in the form of a wobble plate, there being arranged between the wobble plate and the pistons a non-rotating take-up plate mounted opposite the wobble plate.
Reference is made, furthermore, to the following prior art:
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- DE 2 524 148
- U.S. Pat. No. 4,815,358
- U.S. Pat. No. 4,836,090
- U.S. Pat. No. 4,077,269
- U.S. Pat. No. 5,105,728
In the case of the compressors described in those publications, the purpose is, inter alia, to take measures to prevent or reduce drive mechanism imbalance in use. Otherwise the known arrangements have in common the fact that the rotating components are of relatively large and, consequently, heavy construction compared to the parts moved in translation, namely the pistons, piston rod etc.. Furthermore, the known arrangements have in common the fact that the actual tilt plate apparatus is acted upon by an additional plate by means of a suitable coupling mechanism. The several rotating components are intended to bring about a righting moment of the tilt plate apparatus in the direction of minimum piston stroke, which has an influence on the regulation behaviour.
The mentioned arrangements are all relatively complicated, expensive and of low compactness and for that reason they are unsuitable for the compressors required nowadays by the automobile industry for air-conditioning systems.
Also in the case of mass-produced compressors as are used in motor vehicles, it is an objective that the components moved (especially their mass) should be suitably dimensioned in order to achieve a desired regulation behaviour. The compressor 6SEU 12C mass-produced by DENSO has, for example, a drive mechanism having the following masses relevant to the regulation behaviour:
From the above-mentioned figures it can be seen that a considerable component mass is provided for the parts moved in rotation. By that means an attempt is made to produce a sufficient counter-force or counter-moment relative to the masses moved in translation. The same basic idea also underlies DE 198 39 914 A1, in which indeed the rotating mass of the tilt plate or of the pivotal part thereof is so dimensioned that the centrifugal forces occurring on rotation of the drive plate are sufficient to counteract the pivotal movement of the tilt plate to provide deliberate regulation and consequently to influence, namely to reduce or to limit, or especially to keep constant, the piston stroke and accordingly the quantity delivered.
The influences acting as moments about the tilt centre of a tilt plate apparatus are, in detail, the following moments, the direction of the moments being given in brackets, with (−) denoting down-regulation (in the direction of minimum stroke) and (+) denoting up-regulation (in the direction of maximum stroke):
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- moment due to gas forces in the cylinder spaces (+)
- moment due to gas forces from the drive mechanism chamber (−)
- moment due to a restoring spring (−)
- moment due to an advancing spring (+)
- moment due to rotating masses (−); including moment due to location of centre of gravity (for example, tilt plate: tilt location≠mass centre of gravity) : can be (+) or (−)
- moment due to masses moved in translation (+)
In relation to the mentioned 6SEU 12C compressor of DENSO, which represents the typical constructional form of a tilt plate compressor, it is to be noted that the mass of such a tilt plate cannot be increased at will in order to modify the regulation behaviour accordingly. This is due to the fact that, in the case of the compressors of the described kind, the mass centre of gravity of the tilt plate is generally a substantial distance away from the tilt-providing articulation of the tilt plate. The basic justification for such an arrangement is that the tilt plate, in addition to its own guideway on the drive shaft, has to be coupled to the drive shaft or a component connected to the drive shaft by way of a positioning mechanism.
The mentioned distance between the centre of gravity of the tilt plate and the tilt-providing articulation thereof results in imbalance of the drive mechanism, especially in dependence upon the tilt plate tilting angle (the centre of gravity moves “in the manner of a swing” beneath the tilt-providing articulation), and in the worst case results in an up-regulating characteristic (so-called “location of centre of gravity”).
Accordingly, in the case of the compressors according to the prior art, and indeed according to both the published and the actually practised prior art, a compromise has to be reached so that a predetermined mass of the tilt plate is made available in order to produce a counter-moment to the masses moved in translation; on the other hand, however, the mass of the tilt plate must not be over-dimensioned because then the imbalance of the drive mechanism would be excessive. Otherwise, when a tilt plate is constructed in the form of a tilt ring, increasing the mass thereof is restricted by the available space.
In order to address that problem it has also already been proposed that the pistons, that is to say the masses moved in translation, should be constructed as sparingly, that is to say as lightly, as possible, for example using aluminium or other materials of relatively low specific density. In that respect it has also been proposed to use hollow pistons.
Reference is made furthermore to the compressor according to EP 0 809 027 A1, which relates to a particular arrangement of the coupling mechanism between the drive shaft and tilt plate apparatus. The coupling mechanism is designed for high pressure, for example when R744 is used as coolant. Also of importance in this last-mentioned prior art is so-called constant regulation of the delivery quantity. It is proposed that the kinematics of the compressor be so designed that the down-regulating tilting moments acting on the tilt plate should clearly predominate over the upregulating tilting moments. In this context it should be mentioned that the phrase “delivery quantity” is relatively imprecise. The delivery quantity could be considered constant if, for example, on doubling the speed of rotation, the tilt angle of the tilt plate apparatus halves. As a result the delivery quantity would be constant in geometric terms. Of course, other parameters will also then have an effect on the delivery quantity when the tilt angle of the tilt plate changes, for example volumetric efficiency, oil throw-off or the like.
For constant regulation of the delivery quantity in the event of changing speeds of rotation, the restoring torque of the tilt plate apparatus is utilised because the tilt plate opposes its angled position because of the dynamic forces at the co-rotating plate part. This process can be aided by the force of a spring so that the increasing quantity delivered in the case of an increase in the speed of rotation is at least partly compensated by restoration of the angled or pivoted position of the tilt plate.
As already mentioned hereinbefore, such a behaviour can in principle be obtained by, for example, integrating an additional mass into the drive mechanism, the inertia of which mass acts on the tilt plate by way of a coupling mechanism. It was also explained that, in the case of compressors as are used today in motor vehicles, the mass of the tilt plate cannot be increased at will without having to accept other disadvantages. This also holds true, especially, for the teaching according to DE 198 39 914 A1 and EP Application No. 99 953 619. The regulation proposed therein using the mass of the rotating components may result in regulation behaviour as a result of which the delivery output is substantially independent of the speed of rotation but this is not necessarily the case. Over-compensation may also be an outcome. The design criteria are very imprecise. The reason for that lies in the fact that the righting moment of the tilt plate is influenced only proportionally by the mass of the rotating components but quadratically by the speed of rotation (ω), which is to say that the quantity delivered can be compensated only in the relatively high speed of rotation range (in this case the dynamics play a part) and for exactly 2 speeds of rotation.
Furthermore, compressors are known, especially mass-produced compressors for R134a, wherein the stroke volume has a tendency to increase solely because of the moments of up-regulating and down-regulating mass forces that come into play. In some cases this has to be compensated by means of appropriate regulatory intervention of the regulating valves used. In the case of relatively new developments, especially for CO2 compressors, attempts are made at reversing that behaviour. The necessary regulatory intervention can then be reduced or can even be dispensed with.
For a better understanding, the described tilting behaviour due to variation in the speed of rotation is shown in
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- high pressure 120 bar and suction pressure 35 bar.
Also calculated were the speeds of rotation:
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- 600 rpm, 1200 rpm, 2500 rpm, 5000 rpm, 8000 rpm and 11,000 rpm.
In
Referring to the diagram according to
Also of relevance are the piston mass, the reference diameter on which the pistons are located, and the number of pistons.
The tilt ring preferably has a mass moment of inertia J2=Jη or J=m/4 (ra2+η2+h2/3) which is greater than 100,000 gmm2. Preferably, the mass moment of inertia is greater than J=200,000-250,000 gmm2.
Furthermore, the tilt ring preferably has a mass moment of inertia of
which is greater than 200,000 gmm2, preferably about 400,000-500,000 gmm2.
There is described hereinbelow the derivation of the so-called moment of deviation, which governs the tilting of the tilt plate or tilt ring and which, more particularly, in the case shown is solely responsible for the tilting of the tilt plate or tilt ring provided that the mass centre of gravity of the tilt plate or tilt ring is located both at the tilting point and also at the geometric centre-point of the tilt plate or tilt ring. This represents an ideal case of the arrangement that is to be aspired to. For the derivation of the moment of deviation the following very generally applies, with reference to
Moment of deviation
Jyz=−J2 cos ψ sin ψ+J3 cos ψ sin ψ
The following holds true independently of
Moment due to mass force of the pistons
Moment Msw due to moment of deviation
The variables used above have the following meanings:
Specifically,
It can be seen that the influence of the piston masses predominates, resulting in the up-regulation behaviour of the swash plate or tilt plate with increasing speed of rotation.
In this case, therefore, Mk,ges>MSW.
In this case, Mk,ges<MSW.
This calculation scheme shows that, compared to the calculation relating to
Starting from the mentioned prior art, the problem of the present invention is to provide an axial piston compressor of the kind mentioned at the beginning wherein changes in the speed of rotation have a minimum influence on the tilt plate apparatus of the compressor, that is to say it is not the delivery output but rather the tilt angle of the tilt plate which should be influenced as little as possible by the speed of rotation.
The problem is solved in accordance with the invention by the characterising features of claim 1, advantageous developments and details of the invention being described in the subordinate claims.
The central concept of the present invention accordingly lies in matching the geometry and the dimensioning of the parts moved in translation, on the one hand, and of the parts moved in rotation, on the other hand, to one another so that the moments caused thereby are always of approximately equal magnitude so that the tilt plate tilt angle remains substantially constant in the case of changing speeds of rotation.
As a result, the following advantages are obtained:
-
- advantageous dynamic behaviour: reduced hunting and counter-regulation by valves;
- less spread between the characteristic curves; as a result, each operating point can be optimally considered during design and placed in the characteristic diagram (of particular interest in the case of CO2 compressors because in the case of these compressors, in comparison to R134a compressors, HP (heat pump) operating points have to be taken into account in addition to AC (air-conditioning) operating points);
- by superimposing a moment due to the location of the centre of gravity it is possible to obtain, approximately, the adjusted plots of the characteristic curves and also to displace them in required manner.
The aim in accordance with the invention is accordingly to adjust the sum of the translational and rotary masses to “zero”. From the above-mentioned equations for MSW due to (moment of deviation) and Mk,ges it emerges that when those two moments are equal the influence of the speed of rotation “ω2” is cancelled out.
Furthermore, the inventors have recognised that it is nevertheless not possible to avoid an influence of the tilt angle of the tilt plate. This emerges from the plots of tan(alpha) and sin(2alpha). The plots of those angle functions are shown in
In accordance with the present invention the drive mechanism should be so designed that, at least approximately, the mentioned undesirable behaviour with respect to change in the speed of rotation at different tilt angles is greatly reduced.
The tilting characteristic shown in
The diagram shown in
The diagram shown in
From
As the tilt angle for setting the balance-sheet of the relevant moments to zero there has been selected a medium tilt angle of a=8°.
In order to modify the moment of inertia of the tilt accordingly, the height of the tilt plate was very slightly increased, more specifically from 13.130 mm to 13.404 mm.
The balance-sheet of the moments in the calculation scheme shows balancing of the moments at a tilt angle of 8°. It can also be seen that the individual characteristic curves in the region of relatively low speeds of rotation are very close to one another and even have a slightly down-regulating effect. The curves then have a point of intersection approximately at a tilt angle α=8° and afterwards become separated again with up-regulation behaviour.
The invention and the aim of the present invention will now be described in greater detail with reference to the further Figures. In detail, the Figures show the following:
show the regulation behaviour of a tilt ring drive mechanism which has been so dimensioned that moment balancing occurs at a tilt angle of 16°, wherein the tilt angle of 16° should be equal to αmax. The height of the tilt plate was adjusted to 14.292 mm. It should be mentioned at this point that other tilt plate parameters can also, of course, be used for adjusting the mass moment of inertia. The parameter of “tilt plate height” was, however, selected merely by way of example in order to provide a ready means of comparison.
The regulation behaviour of the tilt plate according to
In the region between a medium tilt angle and the maximum tilt angle, especially at the maximum tilt angle, the sum of moments of the up-regulating and down-regulating mass forces is approximately zero.
At this point it should also be mentioned that the present description relates solely to the mass forces, inertia forces and resulting moments which influence tilting of the tilt plate and are due to the tilt plate and pistons and possible additional components. In the present case there is used a drive mechanism which has only a few component parts. Starting from the example on which this description is based, having a tilt plate, sliding blocks and pistons, more complex designs can also be envisaged, of course, for example a wobble plate compressor. In principle, that which is said here also holds true for those more complex arrangements.
In addition, the balancing of moments described here can be checked without its being necessary to put the compressor into operation. Starting from the above-mentioned basic equation for the balancing of moments it is clear that the characteristic curves can be calculated from the measured geometry and the measured component masses. Where applicable, the centre of gravity of the tilt plate also has to be determined as well.
Each of the curves for 5000 rpm is to be considered as being representative of a group of curves for a particular operating point. When it is taken into account that a particular regulation pressure of at least 2-3 bar above the suction pressure is required, an advantageous regulation behaviour is achieved by the plots having a certain slope which is linear as far as possible over a wide range. As a result it becomes clear that, for all operating ranges, a group of curves located close to one another is located more in the desired region of the plot diagram than regulation curves which drift apart from one another to a relatively great extent, as is shown in
In such negative cases, for example in the case of up-regulation behaviour in accordance with
The pivotal mounting of the tilt ring 107 defines a pivot axis 101 extending in a transverse direction to the drive shaft 104. The pivot axis is defined, moreover, by two mounting pins 102, 103 mounted coaxially on both sides of the sliding sleeve 108 (see
Of significance is the axial support of the tilt ring at the supporting element 109 arranged to rotate together with the drive shaft 104. That support is provided by means of a supporting arc 110 in operative connection with the tilt ring 107. The supporting arc 110 is so constructed that it overlaps an articulated arrangement effective between the pistons and tilt ring, more particularly in such a manner that, irrespective of the inclination of the tilt ring 107, the possibility is excluded of a collision between the tilt ring 107 and supporting arc 110, on the one hand, and a piston foot 111 surrounding an articulated arrangement, on the other hand (see
The supporting surface of the arc 110 extends approximately concentrically to the centre-point of the articulated arrangement effective between the pistons 118 and tilt ring 107. The axial support is accordingly effective outside the afore-mentioned articulated arrangement, with the consequence that the articulated arrangement that is effective between the pistons and tilt ring is not impaired by axial support measures. This is valid especially for the dimensioning of the afore-mentioned articulated arrangement. As in the prior art, the articulated arrangement is defined by two articulating blocks 121, 122 in the shape of segments of a sphere (see
Furthermore, it can be seen that, in the arrangement shown, the pivotal mounting of the tilt ring 107 serves only for transmitting torque and the supporting element 109 serves only for axially supporting the pistons 118 and/or for providing support against gas forces. The transmission of torque is accordingly de-coupled from the axial support of the tilt ring 107.
Also of particular interest is the supporting surface for the supporting arc 110 on the supporting element 109. That supporting surface is in the form of an arcuate or cylindrical bearing surface 123. In order to avoid displacement of the supporting line, when the inclination of the tilt ring 107 changes, that is to say displacement away from the centre of the pistons 118, the supporting arc 110 is mounted so as to be displaceable in a radial direction relative to the tilt ring 107.
In other respects, reference is made, regarding the design of this drive mechanism, to the German Patent Application No. 103 35 159.0 filed by the Applicant.
In accordance with
In the examples hitherto, it has been assumed that the centre of gravity of the tilt ring 107 coincides substantially with the tilt axis, which extends perpendicular to the mid-axis of the drive shaft. Following on therefrom, however, compressors according to the prior art frequently have centres of gravity in the region of the tilt plate where the centre of gravity of the tilt plate does not coincide with the tilt axis. In according with the invention it is possible to envisage the deliberate incorporation of an “offset”. In that case, centres of gravity in the quadrants Q have the following effects:
-
- Q1 (positive z and y co-ordinates): down-regulating
- Q3 (negative z and y co-ordinates): down-regulating
- Q2 (positive z and negative y co-ordinates): up-regulating
- Q4 (negative z and positive y co-ordinates): up-regulating
The z co-ordinate extends parallel to the mid-axis of the drive shaft, preferably along it. The y co-ordinate extends perpendicular thereto.
If no additional compensation of masses is provided, the centre of gravity in the case of arrangements according to the prior art accordingly lies, very frequently, in the fourth quadrant Q4.
It is of course possible that a centre of gravity arranged in any particular quadrant will change shaft side, relative to the mid-axis of the shaft, when the swash plate tilts, with the consequence, for example, that up-regulation behaviour will be transformed into down-regulation behaviour. It has, however, also been found of course that in the region of the shaft axis the centrifugal force and a tilting moment possibly arising therefrom tend to keep themselves within limits.
Overall, with respect to the two moments already mentioned Mk,ges and MSW, which can be compensated for certain tilt angles, a further tilt moment due to centrifugal force comes into effect, which is included as a component in MSW or msw, which is included in the moment of deviation Jyz, which is in turn included in MSW (MSW=Jyz−ω2).
Hereinbelow there will also be described particular arrangements relating to the location of the centre of gravity of the tilt plate:
An “offset” is provided which has an up-regulating effect. This means that the centre of gravity of the tilt plate is located either in the second quadrant or in the fourth, that is to say in Q2 or Q4.
Various cases are shown in
Because of the gas process in real terms and the clearance volumes, which cannot be avoided and which are highly relevant during compression, a kind of maximum or plateau comes about in the region of low tilt angles which does not allow a clear association between pressure and speed of rotation and frequently results in regulation problems.
As a result of the present invention, that influence can be reduced, that is to say the slope of the characteristic curves tends to be somewhat increased.
In
In the case of current designs, attempts are being directed, as already mentioned, at minimising the minimum tilt angle. Accordingly, for example, the minimum tilt angle can be only about 0.6°. Such a range can, however, be very critical for problem-free compressor start-up. An increase in the minimum tilt angle due to an increase in the speed of rotation even by a few tenths of a degree can therefore be very useful.
FIGS. 16 to 19 show further examples of differing centre of gravity locations, from which the following findings are derived:
Depending on the tilt angle, the drive mechanism provides up-regulating or down-regulation behaviour.
In some regions, the characteristic curves are very close together or even lie on top one one another.
The characteristic curves always intersect at one point.
With reference to
At first sight, the regulating characteristic shown has nothing to do with compensation of mass forces because at a low speed of rotation the tilt angle is kept constant. Consequently, to begin with, the compensation of mass forces relates only to the balancing of the moments Mk,ges and MSW at a predetermined tilt angle. The described case of “down-regulating moment due to the location of the centre of gravity” also falls within that category.
Following on therefrom, the invention relates to balancing the moments Mk,ges and MSW and also an additional moment due to the location of the centre of gravity (up-regulating).
To summarise once again, the advantage of the described examples of embodiments compared to the prior art according to, for example
As a result, the speed of rotation of the drive mechanism then has only a moderate influence, if any influence at all, on the characteristic curves associated with the individual speeds of rotation, insofar as the angle functions tan(α) and sin(2α) have an appreciable effect. This effect is, in any case, small for small “α”.
In addition, as a result of the location of the centre of gravity, a different behaviour can be set. Overall, however, the influence of the speed of rotation is considerably reduced.
As a result of the close grouping of the characteristic curves associated with the speeds of rotation in the case of many operating points, dimensioning of, for example, the restoring spring in desired manner is more simple.
With reference to the above-described characteristic and regulation curves it should be pointed out again that for the characteristic of the compressor according to the invention it is of very major importance and also recognition that the characteristic or regulation curves for differing speeds of rotation run approximately parallel to one another. In the case of a characteristic curve plot of such a kind, the conditions according to the invention are met.
Furthermore, it should be pointed out that the tilt angle of the tilt plate or tilt ring 107 changes by about 2° to 4° in the case of an increase in the speed of rotation from minimum to maximum, more particularly especially under the condition of an approximately constant pressure in the drive mechanism chamber. This change means that the tilt angle is practically constant under the given conditions. Likewise, the piston stroke is then also practically constant.
The spring constant of the restoring spring acting on the tilt plate is generally optimised for a particular speed of rotation. In the case of substantial variations in the speed of rotation, this has a disadvantageous effect in the case of conventional compressors, more specifically because of the relatively large spread in the regulatory characteristic curves between minimum and maximum speed of rotation.
In accordance with the invention, however, the regulatory characteristic curves are located very close to one another and run almost parallel to one another. Accordingly, an optimum spring constant can be set for a relatively close group of characteristic curves with the consequence that the spring constant is set, or can be set, almost optimally for all speeds of rotation between the minimum and maximum speeds of rotation. The spring constant is about 40 to 90 N/mm, especially about 40 to 70 N/mm.
Finally it should also be pointed out that, in the calculation of the mass moments of inertia described hereinabove, especially that of the moment of deviation, there should preferably also be taken into account a so-called Steiner component (ys·zs·m), the moment of deviation being described as follows when this is taken into account:
Jyz=Jyz+ys·zs·m
For small tilt angles of the tilt plate, for example of a tilt ring, the Jyz component is smaller than the Steiner component ys·zs·m. The component Jyz always down-regulates the compressor whereas the component ys·zs·m always up-regulates (set by the position in the quadrant Q2, Q4 according to
From the above-mentioned considerations it emerges that the moment of deviation has two components having contrary influences, that is to say both an up-regulating and a down-regulating component.
The components in question come into effect in each case after a threshold tilt angle αG has been exceeded, the following applying for α<αG:
ys·zs·m>Jyz (up-regulating),
and the reverse for α>αG (that is to say, down-regulating).
All features disclosed in the application documents are claimed as being important to the invention insofar as they are novel on their own or in combination compared with the prior art.
Claims
1. A compressor selected from the group consisting of an axial piston compressor, and an axial piston compressor for the air-conditioning system of a motor vehicle, said compressor having a housing and, operative to draw in and compress a coolant, a compressor unit arranged in the housing and driven by means of a drive shaft, the compressor unit comprising pistons operative to move axially back and forth in a cylinder block, and a tilt plate, swash plate or wobble plate; or tilt ring operative to drive said pistons and to rotate together with said drive shaft, wherein:
- the geometry and dimensioning of all parts moved in translation, such as axial pistons, piston rods or sliding blocks or the like, on the one hand, and all parts moved in rotation, such as the tilt plate, members for conjoint movement or the like, on the other hand, are such that, for angles selected from the group consisting of any desired tilt angles of the tilt plate and between a predetermined minimum tilt angle and a predetermined maximum tilt angle, the moment due to integers selected from the group consisting of the masses moved in translation, that masses of the pistons, where appropriate including sliding blocks, piston rods or the like, is approximately equal to the moment due to the moment of deviation, that is to say the moment due to the mass inertia of the tilt plate.
2. A compressor according to claim 1, wherein the balancing of moments is set for an angle selected from the group consisting of a predetermined tile angle, a tilt angle α=(αmax−αmin)/2, α=αmax, and a predetermined virtual tilt angle α>αmax.
3. A compressor according to claim 1 wherein the centre of gravity of the tilt plate is located on the tilt axis thereof.
4. A compressor according to claim 1 wherein given division of the space surrounding the drive shaft and the tilt plate into four quadrants, the centre of gravity of the tilt plate is offset into a quadrant selected from the group consisting of a first, front quadrant (Q1) delimited by the drive shaft and the front face of the tilt plate including the piston support and facing the pistons, a second, front quadrant located on the side opposite the first quadrant relative to the drive shaft, a third, rear quadrant arranged relative to the tilt plate at the height of the second quadrant behind the tilt plate, that is to say on that side of the tilt plate which is remote from the pistons, and a fourth, rear quadrant arranged relative to the tilt plate at the height of the first quadrant behind the tilt plate, that is to say on that side of the tilt plate which is remote from the pistons.
5. A compressor according to claim 1, said compressor is down-regulatable in the relatively high speed of rotation range and up-regulatable in the relatively low speed of rotation range.
6. A compressor according to claim 4, wherein the arrangement is such that the location of the centre of gravity moves, with a change in the tilt angle of the tilt plate, from an up-regulating quadrant into a down-regulating quadrant or vice-versa.
7. A compressor according to claim 1, wherein an integer selected from the group consisting of the piston stroke, the tilt angle of the tilt plate, and the piston stroke and the tilt angle of the tile plate is substantially constant in the case of changes in the speed of rotation.
8. A compressor according to claim 1, wherein the speed-of-rotation-dependent characteristic curves of the drive mechanism chamber pressure difference, relative to the suction pressure, set against the tilt angle of the tilt plate have a relationship selected from the group consisting of intersecting at one point, and converging at one point.
9. A compressor according to claim 8, wherein the point of intersection of the characteristic curves separates the up-regulating from the down-regulating speed of rotation range.
10. A compressor according to claim 1, wherein the characteristic curves (regulation curves) for different speeds of rotation run approximately parallel to one another.
11. A compressor according to claim 1, wherein the tilt angle of the tilt plate or tilt ring changes by about 2° to 4° in the event of a change in the speed of rotation from minimum to maximum, especially under the condition of an approximately constant pressure in the drive mechanism chamber.
12. A compressor according to claim 1, wherein the spring constant of a restoring spring acting on the tilt plate or tilt ring is selected from the group consisting of between about 40 and 90 N/mm, and of between about 40 and 70 N/mm, the selected spring constant having been optimised for a group of regulation characteristic curves.
13. A compressor according to claim 1, wherein the moment of deviation, taking into account a so-called Steiner component, includes both an up-regulating and a down-regulating term, those terms predominating, in each case, after a threshold tilt angle of the tilt plate has been exceeded, especially, in the case of
- α<αG in up-regulating manner, and
- α>αG in down-regulating manner.
Type: Application
Filed: Oct 5, 2004
Publication Date: Sep 27, 2007
Inventors: Otfried Schwarzkopf (Magstadt), Michael Arnemann (Karlsruhe)
Application Number: 10/575,885
International Classification: F04B 1/12 (20060101);