DE102004027321A1 - axial piston - Google Patents

Abstract

Axial piston compressor, in particular compressor for the air conditioning system of a motor vehicle, comprising a housing 10 and a housing 10 driven via a drive shaft 11 driven compressor unit for sucking and compressing a refrigerant, wherein the compressor unit in a cylinder block 12 axially reciprocating piston 13 and a swash plate (swiveling ring, swash plate or swash plate 14) which drives the pistons 13, the swash plate 14 being assigned an additional mass 15, by means of small tilt angles of the swash plate 14, in particular in a tilt angle range of 0 ° to 8 DEG, in particular 0 DEG to 3 DEG, a Deviationsmoment the swash plate 14 largely rectified Deviationsmoment is obtained, such that the tilting moment of the swash plate 14 is increased as a result of Deviationsmoments same in the biased Kippwinkelbereich in order in this way the Ausl To support the swashplate 14 out of a range of small tilt angle out (accelerated Aufsteller the compressor).

Description

The The invention relates to an axial piston compressor, in particular compressor for the Air conditioning system of a motor vehicle, with a housing and arranged in the housing, via a Drive shaft driven compressor unit for suction and compression a refrigerant, the compressor unit axially in and out of a cylinder block running piston and a piston driving, rotating with the drive shaft Swash plate, e.g. in the form of a swivel ring, a wobble or swash plate, includes.

Such axial piston compressor is for example from the DE 197 49 727 A1 known. This includes a housing in which a plurality of axial pistons are arranged around a rotating drive shaft in a circular arrangement. The driving force is transmitted from the drive shaft via a driver on an annular pivot plate and from this in turn to the parallel to the drive shaft translationally displaceable piston. The annular swash plate is pivotally mounted on a sleeve mounted axially displaceably on the drive shaft. In the sleeve, a slot is provided through which engages the mentioned driver. Thus, the axial mobility of the sleeve on the drive shaft is limited by the dimensions of the elongated hole. An assembly takes place by a passing through the driver through the slot. Drive shaft, driver, sliding sleeve and swivel disk are arranged in a so-called. Engine room in which a gaseous working fluid of the compressor is present at a certain pressure. The delivery volume and thus the delivery rate of the compressor are dependent on the pressure ratio between the suction side and pressure side of the piston or correspondingly dependent on the pressures in the cylinders on the one hand and in the engine room on the other.

A slightly different type of axial piston compressor is for example in the DE 198 39 914 A1 described. The swash plate is designed as a swash plate, wherein between the swash plate and the piston mounted opposite the swash plate, rotatable receiving disc is arranged.

From the EP 1 172 557 A2 is the in 13 shown compressor known. This has a swash plate device with a swash plate in the form of a swash plate 118 on, on the pistons 120 over sliding blocks 121 are articulated. Furthermore, the swashplate device has a support device, which at the same time as a driver component, a torque between a drive shaft 114 and the swash plate 118 transfers.

One on the drive shaft 114 fixed first driver component 117 in the form of a bearing of the Mitnehmerbauteils, which is designed as a receiving bore is at a considerable distance next to the swash plate 118 arranged, and a second, in the first hingedly engaging driver component 119 is as a lateral extension of the swash plate 118 educated. The above-described structure of the swash plate in the form of paired driving components 117 and 119 ensures an exposed center of gravity of the swash plate device. The center of gravity, which is remote from the tilting axis and also the tilting joint, causes an imbalance since the engine can only be balanced for a preferably medium swashplate tilting angle. It should be noted that the center of gravity in response to the tilt angle at a considerable distance to the tilting joint, which is the center of the pivoting movement moves. The swash plate 118 also has a thickened hub part and, as explained above, one through the driver components 117 and 119 conditional relatively large moment of inertia with a center of gravity significantly away from the tilt axis, so that a sudden change in the rotational speed with appropriate inertia to a tilt adjustment of the swash plate 118 leads.

Furthermore, the center of gravity essentially determines a control behavior. The control behavior is influenced in such a way that the compressor greatly up-regulates, ie the inertia forces of the swash plate and their center of gravity cause a deviation moment J, which in turn generates a tilting moment M _SW = J × ω ² . The aforementioned tilting moment is always opposite to the deviation moment J. As a rule, this means in the case of compressors according to the prior art, a Kippwinkelverringerung, especially in the work area at medium and larger tilt angles. In general, of course, different moments of deviation act on a component, the deviation moment mentioned here being the deviation moment relevant to the tilting movement of the swashplate. This moment of deviation is caused by the only degree of freedom in the system that is caused by the tilting joint.

A construction such as that described above is implemented, for example, in the DENSO series compressor 6SEU 12 C in which R134a is used as the refrigerant. The (relevant) Deviationsmo ment J of the swash plate causes a tilting moment M _SW about the center of the tilting movement of the swash plate, which is so effective at least in the range of medium and larger oblique plate tilt angle, that seeks to reduce the tilt angle of the swash plate. The mass forces of the piston cause (via their deflection) on the swash plate a tilting moment M _{k, ges} , which is also effective around the center of the tilting movement of the swash plate. In contrast to the tilting moment of the swash plate M _SW , the tilting moment generated by the pistons acts in the direction of increasing the tilt angle of the swash plate. The center of gravity of the system, which is outside the tilt or pivot point of the swash plate, additionally supports the effect of the piston. The effect of the center of gravity is generally included in the calculation of the (total) moment of deviation, where it is taken into account via a so-called Steiner proportion.

In with reference to the mentioned DENSO compressor 6SEU 12 C should be noted that the mass a swash plate can not be increased arbitrarily to the control behavior of a compressor to change. That's because of that the compressors of the type described the center of gravity of the swash plate usually a clear distance to the tilting joint of the swash plate having. This construction is essentially based on that the Swing plate additionally to a suitable leadership on the drive shaft over an actuating mechanism with the drive shaft or one with the drive shaft connected component must be coupled (driver component).

Of the mentioned Distance from the center of gravity of the swash plate and the tilting joint of the same leads to an imbalance of the engine, in particular depending from the swivel tilt angle (the center of gravity moves "as in a swing "below the tilting joint), and leads in the worst case Fall to an up-regulating property (so-called "center of gravity").

Future compressors should be in the area of the swash plate no exposed center of gravity have and imbalance as a result of the engine, in particular caused by the swash plate should be low or ideally be zero.

• – Moment infolge der Gaskräfte in den Zylinderräumen (+)
• – Moment infolge der Gaskräfte aus dem Triebwerksraum (–)
• – Moment infolge einer Rückstellfeder (–)
• – Moment infolge einer Aufstellfeder (+)
• – Moment infolge rotierender Massen (–); inklusive Moment infolge Schwerpunktlage (zum Beispiel Schwenkscheibe: Kipp-Position ≠ Massenschwerpunkt): kann (+) oder (–) sein
• – Moment infolge der translatorisch bewegten Massen (+)

In general, it is the following moments that have in the center of the tilting movement of the swash plate influence on the tilting of the swash plate. In parentheses the direction of the moment is indicated, where (-) means decreasing (in the direction of the minimum stroke) and (+) increasing (in the direction of the maximum stroke).

• - moment due to the gas forces in the cylinder chambers (+)
• - moment due to the gas forces from the engine room (-)
• - moment due to a return spring (-)
• - moment due to an erection spring (+)
• - moment due to rotating masses (-); including moment due to center of gravity (eg swashplate: tilting position ≠ center of gravity): can be (+) or (-)
• - moment due to translationally moving masses (+)

at Speed fluctuations and at the same time largely constant operating conditions affect only the last two moments, namely the Moment due to the rotating masses and the moment due to the translationally moving masses the control behavior. decisive Here, in particular, is the balance of forces and moments around the center the tilting movement of the swash plate.

at Compressors of modern design, it is desirable in the range of small Schwenkscheibenkippwinkel to provide an adjusting moment while at medium and larger tilt angles a clearly off-setting moment for the swivel disc favors becomes.

In this context, be on the EP 0 809 027 It should be noted that in compressors it is desirable to provide constant control of the delivery rate. In the aforementioned document is proposed to design the kinematics of a compressor so that the acting on the swash plate of the compressor abregelnden tilting moments clearly dominate compared to the auftrollden overturning moments.

there it should be noted that the Term "flow rate" relatively blurred is. The delivery rate could be as be considered constant when e.g. when doubling the speed halved the tilt angle of the swash plate. That would be geometric the flow rate constant. Naturally Other parameters also affect the flow rate when the Tilt angle of the swashplate changes, e.g. Degree of delivery, oil throw od. Like.

For a constant control the flow rate with changing rotational speeds, the restoring torque of the Pivoting disc exploited because the swash plate of its inclination due to the dynamic forces counteracts the co-rotating disk part. This behavior can be supported by the force of a spring, so that at increasing speed of rotation or speed increasing flow by default the slant or pivot position of the swash plate at least partially compensated becomes.

For better understanding, the tilting behavior described as a result of a speed fluctuation in the 1 and 2 shown. 1 shows the dependence of the engine room pressure difference with respect to the suction pressure on the tilt angle α or "alpha" of the swash plate.
High pressure 120 bar and suction pressure 35 bar.

Calculated was still at speeds:
600 rpm, 1200 rpm, 2500 rpm, 5000 rpm, 8000 rpm and 11000 rpm.

To recognize are in 1 but only five of the six calculated courses. This is because the gradients for the speeds of 600 rpm and 1200 rpm are substantially completely superimposed (due to lack of dynamics); Therefore, the promoted in the art "speed-independent flow rate" is rather a wishful imagination, which is not met with the measures outlined.

Based on the diagram according to 1 can be easily seen that arise gradients that cause an adjustment of the swashplate to larger tilt angles, as the speed increases. It should be mentioned that 1 only to be considered as an example with simple geometry. However, the trend shown also applies to more complex geometries. The calculation was based on a pivot ring with a predetermined inner and outer diameter and a predetermined height.

Besides the piston mass is relevant, the pitch circle diameter on which the pistons are, and the number of pistons.

The pivoting ring preferably has a mass moment of inertia J ₂ = Jη or J = m / 4 (r _a ² + r _i ² + h ^2/3 ), which is greater than 100,000 gmm ² . Preferably, the moment of inertia is greater than J = 200,000 - 250,000 gmm ² .

Furthermore, the swivel ring preferably has a mass moment of inertia of J ₃ = Jζ = m / 2 (r _a ² + r _i ² ), which is greater than 200,000 gmm ² , preferably about 400,000 - 500,000 gmm ² .

(Anmerkung: J₃ ≈ 2 J₂
Ziel: J_yz soll eine bestimmte Größe haben J_yz ↑ } J₃ ↑ J₂ erhöht sich zwangsläufig!)Below is the derivation of the so-called. Deviationsomomentes specified, which is relevant for the tilting of the swash plate or a swivel ring, and in the case shown solely for the tilting of the swash plate or the swivel ring is responsible under the condition that the center of gravity of the swash plate or of the pivot ring is located both in the tilting point and in the geometric center of the swash plate or the swivel ring. This is a desirable ideal case of construction. For the derivation of the moment of deviation applies in general with reference to 3 : J Y Z = -J 1 cos 2 cos 3 - J 2 cosβ 2 cosβ 3 - J 3 cosγ 2 cosγ 3 α ₁ = 0
β ₁ = 90 °
γ ₁ = 90 °
Direction angle of the x-axis with respect to the main axes of inertia ξ · η · ζ
α ₂ = 90 °
β ₂ = ψ
γ ₂ = 90 ° + ψ
Direction angle of the y-axis with respect to the main axes of inertia ξ · η · ζ
α ₃ = 90 °
β ₃ = 90 ° - ψ
γ ₃ = ψ
Direction angle of the z-axis with respect to the main axes of inertia ξ · η · ζ

(Note: J ₃ ≈ 2 J ₂
Goal: J _yz should have a certain size J _yz ↑} J ₃ ↑ J ₂ inevitably increases!)

of inertia

• J Y Z  = -J 2 cosψsinψ + J 3 cosψsinψ

Moment Msw infolge Deviationsmoment

Independent of 3 applies: moment due to inertia of the piston

Moment Msw due to moment of deviation

θ

Drehwinkel der Welle (wobei die vor- und nachstehenden Betrachtungen der Einfachheit halber für θ=0 angestellt werden)

η

Anzahl der Kolben

R

Abstand der Kolbenachse zur Wellenachse

ω

Wellendrehzahl

α

Kippwinkel des Schwenkringes/Schwenkscheibe

mk

Masse eines Kolbens inklusive Gleitsteine bzw. Gleitsteinpaar

mk,ges

Masse aller Kolben inklusive Gleitsteine

msw

Masse des Schwenkringes

ra

Außenradius des Schwenkringes

ri

Innenradius des Schwenkringes

h

Höhe des Schwenkringes

ρ

Dichte des Schwenkringes

V

Volumen des Schwenkringes

β_i

Winkelposition des Kolbens i

zi

Beschleunigung des Kolbens i

Fmi

Massenkraft des Kolbens i (inklusive einem Gleitsteinpaar)

M(Fmi)

Moment infolge der Massenkraft des Kolbens i

Mk,ges

Moment infolge der Massenkraft aller Kolben

Msw

Moment infolge des Aufstellmomentes des Schwenkringes/Schwenkscheibe bzw. infolge des Deviationsmoments (J_yz)

J

= f(ρ, r, h) Massenträgheitsmoment

The sizes used above mean something like this:

θ

Angle of rotation of the shaft (the above and following considerations are for simplicity θ = 0)

η

Number of pistons

R

Distance of the piston axis to the shaft axis

ω

Shaft speed

α

Tilt angle of the swivel ring / swashplate

mk

Mass of a piston including sliding blocks or pair of sliding blocks

mk, ges

Mass of all pistons including sliding blocks

msw

Mass of the swivel ring

ra

Outer radius of the swivel ring

ri

Inner radius of the swivel ring

H

Height of the swivel ring

ρ

Density of the swivel ring

V

Volume of the swivel ring

β _i

Angular position of the piston i

zi

Acceleration of the piston i

Fmi

Mass force of the piston i (including a sliding block pair)

M (Fmi)

Moment due to the mass force of the piston i

Mk, ges

Moment due to the mass force of all pistons

msw

Moment due to the installation torque of the swivel ring / swashplate or due to the moment of deviation (J _yz )

J

= f (ρ, r, h) mass moment of inertia

Specifically, the lay 1 following tilting moment determination of the swivel or swash plate, where α was varied from 0 ° to 16 °: tilting torque determination swash plate

It let yourself recognize that the Influence of Piston masses outweighs and thus the aufregelnde behavior of the oblique or Pivoting disc at increasing speed results.

It is thus the case M _{k, ges} > M _sw

In 2 is a diagram for a nearly identical engine specified, this diagram is based on the following calculation scheme, in which case α was varied from 0 ° to 16 °: tilting torque determination swash plate

Here is the case M _{k, ges} <M _sw .

This calculation scheme shows that compared to the calculation 1 the thickness or height of the inclined or swashplate of 10 mm ( 1 ) to 18 mm ( 2 ) has been increased. This has the consequence that the relevant moment of inertia J _z increases to approximately twice the value. In 2 is a derating behavior of the swashplate engine to recognize. This trend is indicated by the arrow "n" in 2 , where "n" means the rotational speed of the swash plate or drive shaft, of course, the arrow "n" in the same meaning 1 , only there is the arrow reversed, causing a Aufregeln to be displayed with increasing speed.

The 1 reflects the state of the art. Here, the aufrichtende behavior is appropriate 1 Frequently detectable in current R134a series compressors. In more recent developments, one tries rather to convert this trend into the opposite, namely accordingly 2 ,

In 4 is still the case shown, in which the abregelenden overturning moments due to the moments of inertia / Deviationmomente the swash plate or the swash plate assembly are dimensioned so that a control behavior results in which at an increase in speed of the tilt angle of the swash plate remains almost constant, or decreases , thereby at least a part of the resulting alone by the speed increase resulting flow is compensated.

The representation in 4 the following calculation is used:

In the 5 . 6 and 7 are the ones to 1 . 2 and 4 corresponding tilting moments M _SW , M _{k, ges} and the sums of the two aforementioned moments for a speed in dependence on the tilt angle of the swash plate or the geometric displacement of the compressor shown. In 5 one can see the aufsprennende characteristic of the compressor well on the basis of the momentum sum in the positive range, while in 6 the momentum sum is negative for all tilt angles of the swash plate. A compressor according to the course of the moments 6 follows, has abregde characteristic. Finally, be up 7 which represents a torque curve at approximately instantaneous equality of M _{k, ges} and M _SW , so that the momentum sum is approximately zero for all tilt angles of the swash plate.

In 8a is the sum M _SW + M _{k, ges} indicated for different speeds. 8a corresponds to the 1 and 5 , and clearly shows the rising momentum for increasing speeds, aufzustende total moment.

In 8b is the sum mentioned above for the in the 2 and 6 illustrated case, it can be seen that with increasing speeds, an increasingly regulating moment is obtained.

It should be noted that the Deviationsmoment the swash plate in the case of 8a and 8b is zero at the tilt angle 0 °. That is, in this example, tilting joint and center of mass coincide in the swash plate, and no exposed center of gravity occurs.

The diagram in 8c shows the behavior of a compressor, in which the Deviationsmoment and the resulting tilting moment M _SW + M _{k, ges} at a tilt angle of the swash plate of 0 ° is not equal to zero. This results in that the compressor start is supported by a moment, however, the following problems arise: The fact that at a very small tilt angle of, for example 0 ° already M _SW + M _{k, ges is} not equal to zero, the above-mentioned amount is reflected over the entire tilt angle range again. The curve is therefore compared with a curve with a starting value of M _SW + M _{k, ges} equal to zero shifted approximately parallel. Furthermore, it should be noted that in the area of greater tilt angle of the aufzustere effect is enhanced by the additional tilting moment (see 8a ). Since with modern compressors the trend goes to a regulation behavior, which rather the course of the 2 and 6 respectively. 4 and 7 follows, an adjusting behavior in the range of larger tilt angles is undesirable.

task The present invention is to provide a compressor, in the deflection of the swash plate is supported out of a range of small tilt angles, while undesirable Concomitants such as an imbalance or increased deflection the swash plate for larger tilt angles should be avoided.

This object is achieved by the characterizing features of claim 1, wherein advantageous developments and structural details of the invention be in the dependent claims are written.

An essential aspect of the invention is to assign the swash plate an additional mass through which a Deviationmoment the swash plate largely rectified Deviationsmoment is obtained in a range of small tilt angle of the swash plate. It is a moment that is caused by an erection of the additional mass and a torque M _SW , which is due to an erection of the swash plate is largely rectified. The above-mentioned area of small tilt angles comprises in particular the range of 0 ° to 3 °, preferably even an even smaller tilt angle range of the swash plate, namely the range of 0 ° to 3 °. The additional moment of inertia obtained by the additional mass causes the tilting moment of the swashplate to be increased in the region of small tilting angles, preferably in the range of the abovementioned tilting angles, in order to assist in this way the deflection of the swashplate out of this range of small tilting angles. This allows an accelerated Aufsteller the compressor. Characterized in that an additional mass Devorational torque attributable to the additional mass is obtained only in the range of small tilt angle, the Aufsteller the compressor is facilitated, while in the range of large tilt angle no negative effects such as an imbalance or undesirable control behavior occur.

In a preferred embodiment the additional mass is rotatably coupled to the drive shaft, however relative to this about an axis transverse to the axis of the drive shaft tiltable stored. This provides a structurally simple implementation possibility a compressor according to the invention Preferably, the tilting movement of the additional mass is independent of the tilting movement of the swashplate, resulting in an optimized distribution the moments of deviation and the tilting moments that occur in the system can be achieved. It should be noted that by the measure explained above the Tilt angle of swashplate and additional mass quasi from each other be decoupled, whereby, for example, the additional mass at a Tilt angle of the swashplate of 0 ° a clearly different from 0 ° Can have tilt angle. This is an optimized, desired distribution the involved deviations moments ensured.

In a further preferred embodiment has the additional mass ring or disc shape. That So that's a construction chosen is in which the additional mass in the form of a disc or a ring the swashplate mechanism is coupled, wherein the aufzustende Tipping moment of the disc or the ring with the adjusting tipping moment cooperates due to the Deviationsmoments the swash plate. In the simplest case of coupling, the moments add up. This means that Defined by the additional mass Deviationsmoment the moment of deviation superimposed on the swash plate becomes. It is natural also a construction conceivable in which the additional mass no moment transfers to the swash plate, but a power transmission takes place, such that a Reaction force is created on the swash plate, which is a corresponding Additional deviation moment triggers. This is preferably the case in the embodiment in which the tilting movement of the additional mass regardless of the tilting movement of the swash plate is. It should also be noted that the additional mass, the like mentioned preferably in the form of an additional disc or an additional ring is present, is optimized in such an advantageous manner that the ratio of their moment of inertia and their component mass as possible is great. The component mass should therefore as possible be low with the largest possible Inertia. To achieve this, is suitable as additional mass in particular a Additional ring with an outer diameter, only slightly smaller than the inner diameter of the engine casing; if other limiting factors for the diameter exist are the greatest possible outer diameter of such a ring desirable. If there is a ring, the outer circumference is this ring is preferably made spherical in cross-section to a collision between the additional ring and the engine housing or another component of the compressor during pivoting of the Additional ring around its tilt axis to avoid. The distance between Additional ring and a housing inner wall should preferably be independent be substantially constant from the tilted position of the additional ring.

Preferably the additional mass is partially or substantially within a recess arranged the cylinder block. This ensures on the one hand the roundabouts the additional mass to the swash plate, while on the other side through the recess in the cylinder block Compressor with one possible low weight allows becomes.

The center of mass of the additional mass is located in a further preferred embodiment in the region of a tilting joint associated with the additional mass. Preferably, the center of gravity continues to lie approximately on the central axis of the drive shaft. In a further preferred embodiment, the additional mass with a displaceably mounted on the drive shaft sleeve in operative engagement, wherein the vorste Hend said sleeve in turn is in operative engagement with a guide or joint bush of the swash plate mechanism. By such a construction, a reliable transfer of force from the additional mass on the swash plate mechanism is guaranteed; In this case, a force is transmitted from the additional mass to the swash plate, which induces an additional moment of deviation in the same. Such a construction is characterized in that it is robust and error-prone.

The Additional mass preferably has sites of reduced material accumulation so that she at a tilt angle of the swashplate of 0 ° has its greatest deviation moment. Reduced accumulations of material are in particular due to recesses and / or pockets and / or grooves and / or holes realized. By such a design becomes an optimal Aufregelverhalten the compressor according to the invention ensured, it being noted that the moment of deviation the swash plate at a tilt angle of 0 ° expediently clearly from zero different.

In a further preferred embodiment is one of the additional mass associated tilting by at least limited to a stop arranged on the drive shaft. By attaching a stopper is done with simple constructive means made sure that the Tilting area is not over the wished Frame goes out. Preferably, the stop or are the associated attacks formed in the form of a paragraph of the drive shaft, which is a constructive simple, material-saving variant of a construction according to the invention represents.

The additional mass preferably looks in such a manner with the swashplate in operative engagement, that largely results in a total torque, which corresponds to the sum of two individual moments, namely the moment M _{SW of} the swash plate and a torque corresponding to this M _{SW, Z of} the additional mass. This ensures optimum distribution of the moments in a compressor according to the invention.

The Invention will be described below with regard to further advantages and Features by way of example and with reference to the enclosed Drawings described. The drawings show in:

9 a compressor according to the invention in longitudinal section, wherein the engine is in a position for minimum piston stroke;

9a a detailed view of a section of the in 9 illustrated compressor;

10 a compressor accordingly 9 wherein the engine is in a position where the piston stroke is maximum;

10a a detailed view of a section of the in 10 illustrated compressor;

11 the engine of the compressor according to the 9 and 10 in a perspective exploded view; and

12 a representation of the responsible for the tilting movement of the swash plate Deviationsmoments depending on the tilt angle thereof.

The in the 9 and 10 in longitudinal section axial piston compressor for the air conditioning of a motor vehicle comprises an engine housing 10 , which is cup-shaped, and at the peripheral edge of a cylinder block 12 followed. Inside the cylinder block 12 are several, preferably 5 . 6 or 7 arranged axially reciprocating piston, wherein the distribution of the piston around the housing center axis 18 is uniform around. Through the bottom of the cup-shaped housing 10 through one extends over a pulley 21 driven drive shaft 11 in the interior of the housing or in an engine room 22 into it. The storage of the drive shaft takes place on the one hand in the region of the bottom of the cup-shaped housing 10 and on the other hand inside the cylinder block 12 , Within the engine compartment, a swashplate mechanism is operative to control the rotational movement of the drive shaft 11 in axial movement of the piston 13 is implemented. For this purpose, engages a swash plate in the form of a swash plate 14 with its peripheral edge via a hinge assembly in C-shaped recesses on the back of the piston 13 one. The joint arrangement is as well as in the prior art by two spherical segment-like joint stones 16 . 17 defined, between which the swash plate 14 sliding intervenes. The spherical bearing surfaces of the joint stones 16 . 17 are corresponding spherical hollows on the facing each other End faces of the C-shaped recesses of the piston 13 assigned. Between a cylinder head 2G and the cylinder block 12 intake and exhaust valves are arranged in a conventional manner known for example from the prior art.

The tilt angle of the swash plate 14 is between the positions according to 9 and according to 10 changeable, with in 9 the tilt angle of the swash plate 14 minimal and in 10 is maximum. Corresponding to the stroke of the piston 13 minimum or maximum.

The swash plate 14 is an additional mass in the form of an additional disc 15 assigned. The additional mass in the form of additional disk 15 is about a joint in the form of two bolts 19 (compare in particular 11 ) on the drive shaft 11 attached. The additional disc 15 is in a recess 18 in the cylinder block 12 arranged. This ensures a compact design of the compressor, wherein in addition by the recess in the cylinder block a weight saving is realized.

The additional disc 15 is tiltably mounted with respect to an axis of the joint by means of which it is attached to the drive shaft. The additional disc 15 can be tilted in a range of 0 ° to 3 ° about the aforementioned axis, which is transverse to a drive shaft center axis 20 extends, which simultaneously represents the central axis of the housing. The angle of maximum deflection is determined by a stop 23 in the form of a shoulder on the drive shaft 11 established. The additional disc 15 stands with part of their engine room 22 facing surface 24 with a sleeve 25 in operative engagement, which in turn is operatively engaged with a pivot bushing of the swashplate mechanism. Accordingly, the tilting moment causes the additional disc 15 a force F (in 9a indicated), which induces a tilting moment in the swash plate mechanism in the direction of a larger tilt angle.

By limiting the working area of the additional disc, by the stop 23 is conditional, the swivel mechanism and the mechanism of the additional disc 15 separated from each other at a tilt angle of 3 °. This means, in other words, that the swashplate including its additional mass is supported at a minimum tilt angle when truing up, while at larger tilt angles, the additional disc assisting the tensing up 15 has no influence on the control behavior of the United poet more. To cope with the control behavior of a modern compressor is the swash plate 14 or the entire swashplate mechanism designed such that, in particular at large tilt angles and high speeds, the swash plate has a abregard tendency. It should be noted at this point that at the point at which the intervention of the additional mass is limited or reaches its limits, either a slight jump in the course of the total tilting moment is conceivable or not (see 12 , in which the adjusting moment of deviation in dependence of the tilt angle of the swash plate 14 is shown). Depending on requirements, the corresponding technical realization can be selected. It should also be noted that various coupling mechanisms are conceivable, including that the moment of the additional mass is initiated directly. Out 12 is also apparent that the aufzustende Deviationsmoment for a tilt angle of the swash plate 14 of 0 ° is maximum.

In 11 is the engine according to the 9 and 10 shown in exploded view. The additional disc 15 is, as already in the description of the 9 and 10 indicated by means of two hinge pins 19 on the drive shaft 11 tiltably mounted in a direction transverse to its longitudinal extent.

Even though the invention based on embodiments is described with a fixed combination of features, but it includes also the conceivable further advantageous combinations of these features, as specifically, but not exhaustively, indicated by the subclaims are. All Features disclosed in the application documents are considered to be essential to the invention as far as they are individually or in combination with respect to State of the art are new.

10

casing

11

drive shaft

12

cylinder block

13

piston

14

swash plate

15

additional disk (Auxiliary mass)

16

slide

17

slide

18

recess in the cylinder block

19

pintle

20

Drive shaft center axis

21

pulley

22

Machine Room

23

attack

24

the engine chamber facing side of the additional disc 15

25

shell

26

cylinder head

114

drive shaft

117

first driving component

118

swash plate

119

second driving component

120

piston

121

slide

Claims (10)

Axial piston compressor, in particular compressor for the air conditioning system of a motor vehicle, having a housing ( 10 ) and one in the housing ( 10 ), via a drive shaft ( 11 ) driven compressor unit for sucking and compressing a refrigerant, wherein the compressor unit in a cylinder block ( 12 ) axially reciprocating pistons ( 13 ) and one the pistons ( 13 ) driving, with the drive shaft ( 11 ) rotating swash plate (swivel ring, swash plate or swash plate ( 14 )), characterized in that the swash plate ( 14 ) an additional mass ( 15 ) is assigned by which in a range of small tilt angle of the swash plate ( 14 ), in particular in a tilt angle range of 0 ° to 8 °, in particular 0 ° to 3 °, a moment (M _SW ) due to a Aufstellmoments the swash plate ( 14 ) largely rectified moment as a result of a Aufstellmoments the additional mass is obtained, such that the tilting moment of the swash plate ( 14 ) is increased in the aforementioned Kippwinkelbereich due to the Deviationsmoments same, in order in this way the deflection of the swash plate ( 14 ) out of a range of small tilt angle out (accelerated Aufsteller the compressor). Compressor according to claim 1, characterized in that the additional mass ( 15 ) with the drive shaft ( 11 rotatably coupled, but relative to this about an axis transverse to the axis of the drive shaft ( 11 ) is tiltably mounted. Compressor according to claim 1 or 2, characterized in that the tilting movement of the additional mass ( 15 ) regardless of the tilting movement of the swash plate ( 14 ). Compressor according to one of the preceding claims, characterized in that the additional mass ( 15 ) Has ring or disc shape. Compressor according to one of the preceding claims, characterized in that the additional mass ( 15 ) partially or substantially within a recess ( 18 ) of the cylinder block ( 12 ) is arranged. Compressor according to one of the preceding claims, characterized in that the additional mass ( 15 ) has its center of mass in the region of a tilting joint assigned to it, the center of mass being approximately at a central axis of the drive shaft ( 11 ) lies. Compressor according to one of the preceding claims, characterized in that the additional mass ( 15 ) with one on the drive shaft ( 11 ) slidably mounted sleeve ( 25 ) is operatively engaged with a guide or pivot bushing of the swashplate mechanism in operative engagement. Compressor according to one of the preceding claims, characterized in that the additional mass ( 15 ) Reduced material accumulation, in particular recesses and / or pockets and / or grooves and / or bores has such that they at a tilt angle of the swash plate ( 14 ) of 0 ° possesses its greatest moment of deviation. Compressor according to one of the preceding claims, characterized in that a tilting region of the additional mass ( 15 ) by at least one on the drive shaft ( 11 ) arranged stop ( 23 ) is limited, which preferably in the form of a shoulder of the drive shaft ( 11 ) is present. Compressor according to one of the preceding claims, characterized in that the additional mass ( 15 ) with the swash plate ( 14 ) is in operative engagement that largely a total moment in the form of the sum of the two moments M _{SW of} the swash plate ( 14 ) and M _{SW, Z of} the additional mass ( 15 ).