Scrollmaschine

Abstract

A scroll machine (2), in particular for refrigerant of a vehicle air conditioning system, comprises: - a first scroll (32) having a first spiral wall (52) projecting in an axial direction (A), - a second scroll (34) with a second spiral wall (54) projecting in the axial direction (A), - a drive (20), - a drive shaft (38) by means of which the drive (20) and the second scroll (34) are coupled in terms of power transmission, and - a radius compensation system (36) which is connected between the drive shaft (38) and the second scroll (34) and which has an eccentric (40) which is coupled to the drive shaft (38) by means of a shaft pin (42) arranged eccentrically to the drive shaft (38) and to the second scroll (34) by means of a bearing pin (40) which is eccentric with respect to the shaft pin (42), wherein the shaft pin (42) is arranged in a first half-field (76) described by a connecting line (72) between a drive shaft axis (70) and a bearing axis (66) of the second scroll (34) with respect to an end face (74) of the drive shaft (38), wherein the radius compensation system (36) has a control weight (44) which is movably coupled to the eccentric (40) by means of a lever arm (80) in a control bearing (82), wherein the lever arm (80) is mounted in a stationary pivot bearing (84) which is arranged in a second half-field (78) separated from the first half-field (76) by the connecting line (72) on the end face (74) of the drive shaft (38), wherein the adjusting bearing (82) is arranged in the second half-field (78) with respect to the end face (74) of the drive shaft (38), and wherein a center of gravity of the adjusting weight (44) is arranged approximately on the connecting line (72).

Description

[0001] The invention relates to a scroll machine, for example in the form of a scroll compressor, which is used in particular for compressing refrigerant in a vehicle air conditioning system.

[0002] Motor vehicles are regularly equipped with air conditioning systems that use a system forming a refrigerant circuit to cool the vehicle interior. Such systems generally have a circuit containing a refrigerant. The refrigerant, for example R-744 (carbon dioxide, CO2) or R-134a (1,1,1,2-tetrafluoroethane), is heated in an evaporator and compressed by a (refrigerant) compressor. The refrigerant then releases the absorbed heat via a heat exchanger before being returned to the evaporator via a throttle.

[0003] A so-called scroll machine is often used as a refrigerant compressor to compress a refrigerant. The design and operation of such a scroll machine, used as a compressor for the refrigerant in a motor vehicle air conditioning system, is described, for example, in DE 10 2012 104 045 A1. Key components of such a scroll machine are two scroll parts (“scrolls”) that can move relative to one another. The system usually also contains oil in droplet form or as a mist, which is at least partially separated from the refrigerant (which is usually gaseous after compression) after compression. The refrigerant (possibly with oil residues) is then introduced into the air conditioning circuit, while the separated oil can usually be fed to the moving parts within the scroll machine to lubricate them.

[0004] The scroll components are typically designed as a stationary, fixed scroll (fixed scroll, displacement scroll) and a movable, orbiting scroll (counter scroll, rotor scroll). Both scrolls are fundamentally similar in design and each comprise a base plate (main body, scroll disk) and a spiral (worm-shaped) wall (spiral wall, scroll wall) extending axially from the base plate. When assembled, the spiral walls of the two scrolls are nested within each other, forming several conveying chambers between the scroll walls, which touch each other in sections.

[0005] An orbiting movement, here and in the following, is understood in particular to mean an eccentric, circular movement path in which the movable scroll itself does not rotate about its own axis. During operation, the two scrolls are kept as close to each other as possible axially. During each orbiting movement, essentially crescent-shaped (compression or delivery) chambers are formed between the spiral walls. As the two scrolls move toward each other (at least during a compression process), their volume migrates from the outside along the spiral walls toward the center axis of the respective scroll, thereby progressively reducing the volume (and thus compressing the medium contained within).

[0006] To drive the movable scroll, an electric motor is typically provided, the motor shaft of which is coupled to the movable scroll part by means of an (A-side) eccentric shaft journal (also: “shaft pin”).

[0007] Due to manufacturing tolerances, including those of the two scroll contours, the actual eccentric track of the movable scroll usually deviates from an ideal eccentric track. To ensure the most consistent radial contact between the two scrolls, particularly their scroll walls, throughout the entire orbital movement, a unit (also known as an "eccentric unit" or "swing link") is usually provided that is rotatably mounted on the shaft journal. This swing link is mounted eccentrically relative to the shaft journal. Specifically, the shaft journal is mounted eccentrically in a bearing journal of the swing link, with the movable scroll, in turn, being mounted rotatably about the bearing journal, usually by means of a rolling bearing.

[0008] During (compressor) operation, tangential compression forces act on the walls (scroll walls) of the delivery chambers. These compression forces also act on the center of the bearing journal. These tangential compression forces must be balanced by a driving or counterforce (particularly to maintain operation, primarily to maintain sufficient sealing between the scroll walls). This counterforce acts at the center of the shaft journal. Due to the offset of the centers of the shaft and bearing journals, a torque is generated that causes the swing link to rotate around the shaft journal. Due to the eccentricity of the bearing journal to the shaft journal, this rotation leads to a radial displacement of the center of the bearing journal relative to the center of the motor shaft. In other words, this changes the so-called orbital radius and thus the radial distance between the scroll walls.The Swing Link therefore forms a radius compensation system.

[0009] However, due to the eccentricity of the movable scroll, an imbalance also occurs during operation. This imbalance causes the movable scroll to press even more tightly against the fixed scroll. Since the imbalance is dependent on the rotational speed, this additional pressure force would cause significantly excessive and undesirable friction between the scroll walls—even with a constant initial pressure but increasing rotational speed. To counteract this problem, counterweights are used, which are usually integrated into the swing link.

[0010] The invention is based on the object of improving a scroll machine.

[0011] This object is achieved according to the invention by a scroll machine having the features of claim 1. Advantageous and partly inventive embodiments and further developments of the invention are set out in the subclaims and the following description.

[0012] The scroll machine according to the invention preferably forms a refrigerant compressor for refrigerant in a vehicle air conditioning system. The scroll machine comprises a first scroll with a first spiral wall protruding in an axial direction and a second scroll with a second spiral wall protruding in the axial direction. The two scrolls are arranged, in particular, with their spiral walls inserted into one another. The scroll machine further comprises a drive and a drive shaft, by means of which the drive and the second scroll are coupled for power transmission. Furthermore, the scroll machine comprises a radius compensation system, which is connected between the drive shaft and the second scroll and which has an eccentric.This eccentric (also known as a swing link) is coupled to the drive shaft by means of a shaft pin (or shaft journal) arranged eccentrically to the drive shaft, and to the second scroll by means of a bearing journal eccentric with respect to the shaft pin. The shaft pin is arranged - at least with its axis - in a first half-field with respect to an end face of the drive shaft, described by a connecting line between a drive shaft axis (also: rotational axis of the drive shaft) and a bearing axis of the second scroll. The radius compensation system also has a control weight which is movably coupled to the eccentric by means of a lever arm in a control bearing. The lever arm is mounted in a stationary pivot bearing (in particular pivotable, i.e. rotatable about the pivot bearing).This pivot bearing is arranged in a second half-field on the end face of the drive shaft, separated from the first half-field by the connecting line. The adjusting bearing is also arranged in the second half-field relative to the end face of the drive shaft. A center of gravity of the adjusting weight (in particular a center of gravity formed by a mass portion of the adjusting weight and by the lever arm of the adjusting weight) is arranged approximately on the connecting line.

[0013] "Arranged approximately on the connecting line" is understood here and below in particular to mean that the control weight—as it is a component intended to be movable—in particular its center of gravity, can be arranged around the connecting line within an angular adjustment range that is intended and required for the intended radius compensation during operation of the scroll machine. This angular adjustment range extends in particular approximately + / -10, in particular approximately + / -5 degrees, on both sides of the connecting line.

[0014] The control weight therefore forms part of the radius compensation system (swing links). The described movable arrangement relative to the eccentric allows for a modified lever arm design compared to classic swing link designs. While classic designs feature a control weight rigidly attached to the eccentric, deflection can now be achieved via the pivot bearing. This allows the force application point on the eccentric to be positioned favorably with a view to a control weight with the lowest possible mass, thus reducing the mass of the control weight. If the force application point of the swing link and / or the pivot bearing is as far apart (especially vertically) as possible from the connecting line compared to the (especially vertical) distance of the shaft pin from the connecting line, it is recognized that a comparatively small mass of the control weight is sufficient to cause the eccentric to rotate.In the case of a rigid connection of the mass of the control weight to the eccentric, an imbalance of the second scroll still occurs (or remains unbalanced during operation), since its center of gravity and pivot points lie on the connecting line, whereas the control weight would be deflected by the connecting line with a rigid connection or is not even positioned on the connecting line at all. Therefore, in the case of the above-described shift in the force application point, the balancing mass - at least part of the balancing mass in the form of the control weight - is no longer positioned on the connecting line and thus (due to incorrect positioning) results in an unbalanced imbalance of the second scroll during operation. To reduce this unbalanced "residual imbalance," a control weight that is as small as possible is advantageous.In this respect, however, it is more advantageous to position the mass of the adjusting weight as far as possible on the connecting line in order to compensate for the imbalance of the second scroll. For this purpose, the invention advantageously provides for the adjusting weight, preferably the lever arm, to be applied to the eccentric, in particular on the side of the end face of the drive shaft opposite the shaft pin across the connecting line (second half-field), and to be mounted by means of the pivot bearing. The deflection caused in this way achieves an effect similar to that of the adjusting weight lying on a straight line between the axis of the shaft pin and the adjusting bearing. A basic function of the swing link, a "torque balance" between the first and second scroll, is still fulfilled. This is because the second scroll generates a torque during operation due to its imbalance, which is to be compensated for by the swing link.Due to the lever arm described above, which is now larger, this compensation can now be achieved with a smaller mass. This lower mass has the further advantage of reducing the rotational inertia, particularly of the second scroll (which is moved by the drive during operation). The second scroll, which tends to snuggle up to the first scroll due to gas force and the swing link mechanism, can now do so particularly responsively thanks to the inventive design.

[0015] According to a preferred embodiment, the pivot bearing is arranged not only in the second half-field, but also in a quadrant of the end face opposite the shaft pin across the drive shaft axis. If the quadrant in which the shaft pin is arranged is referred to as the first quadrant, the quadrant (in a circular counting system) in which the pivot bearing is arranged would be referred to, in particular, as the third quadrant.

[0016] Optionally, the adjusting bearing is also arranged in this quadrant.

[0017] According to a practical embodiment, the pivot bearing, and in particular also the adjusting bearing, is arranged lagging behind the shaft pin with respect to a rotational direction of the drive shaft in a compression mode (when looking from the first and second scroll onto the end face of the drive shaft). For example, the shaft pin - when looking at the end face of the drive shaft as described - is arranged in the area between a nine o'clock and a twelve o'clock position (or: "upper left quadrant"), and the pivot bearing (and in particular also the adjusting bearing) is thus positioned in the half-field between the twelve o'clock and six o'clock positions, optionally between the three o'clock and six o'clock positions (or: "lower right quadrant"). In the event that an opposite direction of rotation of the drive shaft is intended for compression, the shaft pin, adjusting bearing, and pivot bearing are arranged in reverse.

[0018] According to a further preferred embodiment, the pivot bearing is arranged at the edge of the drive shaft. "Edge" is understood here and below to mean, in particular, that the pivot bearing is arranged within the edge-side 50 percent, preferably 30 percent, of the radius of the drive shaft. This advantageously allows for the lever length to be as long as possible for transmitting the centrifugal force (or imbalance) of the control weight.

[0019] According to a particularly expedient embodiment, the pivot bearing is positioned such that a right angle is formed between a straight line between the center of gravity of the actuating weight and the pivot bearing (in particular its axis) - this straight line forms a first section of the lever arm - and a straight line between the pivot bearing and the axis of the shaft pin (i.e. with a tolerance of preferably less than + / - 10 degrees, in particular + / - 5 degrees). This enables the greatest possible distance between the first section of the lever arm and the shaft pin. As a result, the torque of the actuating weight about the pivot bearing can also generate a large force in the shaft pin.

[0020] Furthermore, according to an advantageous embodiment, the adjusting bearing, preferably a contact point of the lever arm in the adjusting bearing, is arranged at least approximately - i.e. exactly or at a distance of a few (e.g. 0.5 to a maximum of 2) millimeters (in a scroll machine with an orbital radius of 5 + / - 1 mm) - on the straight line between the rotary bearing and the shaft pin (axis).

[0021] According to a practical embodiment, the distance between the adjusting bearing (in particular a contact point of the lever arm in the adjusting bearing) and the shaft pin axis is greater than the distance of the shaft pin axis to the connecting line. This, preferably in combination with the edge-side arrangement of the pivot bearing described above, results in a particularly large lever (lever length) between the adjusting bearing and the shaft pin axis, so that the mass of the adjusting weight can be kept low.

[0022] In particular, the center of gravity of the second scroll is on its bearing axis. For manufacturing reasons or other reasons, minor deviations of a few millimeters (e.g., one to two millimeters) are possible in a scroll machine whose movable scroll has an orbital radius of 3 to 8 mm, especially in the range between 4 and 7 mm, but these are negligible.

[0023] According to another practical embodiment, a vertical distance between the connecting line and the pivot bearing is greater than a vertical distance between the connecting line and the shaft pin axis. From a power transmission perspective, this design is advantageous because – especially in combination with the straight line between the control weight and the pivot bearing being perpendicular (or at least almost perpendicular, e.g., within a range of + / - 5 degrees) to the straight line between the pivot bearing and the shaft pin axis – the product of the mass of the control weight and its distance from the (drive) shaft axis can be kept smaller than the product of the mass of the movable scroll and its orbital radius (distance between the shaft axis and the bearing axis).

[0024] According to a preferred embodiment, the lever arm in the adjusting bearing is accommodated by a pin in a slot-like contour formed in the eccentric. In a simple variant, the slot-like contour is an elongated hole. Alternatively, the contour is formed by a slot that opens towards the edge of the eccentric.

[0025] In principle, it is possible for the pin, which is housed in the contour of the adjusting bearing, to be designed as a circular cylindrical pin. However, to enable the most extensive contact possible and thus reduce Hertzian pressure between the pin and the contour—especially compared to a linear contact between the pin and the contour—the pin advantageously has a non-circular profile, i.e., one that deviates from a circular shape.

[0026] According to a practical refinement of the non-circular profile of the pin, the contact surfaces of the pin towards the eccentric (especially flat) form convexly curved sections of a profile approximating a polygon. In particular, the pin is roughly square with outwardly curved side surfaces (comparable to an optical defect known as barrel distortion).

[0027] According to a further expedient development of the non-circular profile of the pin, the contact surfaces of the pin towards the eccentric are shaped according to an involute of a rotational circle of the pin. Corresponding mating contact surfaces of the slot-like contour are preferably shaped according to a corresponding involute (in particular the rotational circle of the eccentric). In this case, the pin and slot (i.e. the slot-like contour) form part of an involute toothing (comparable to a gear pair), so that sliding of the pin in the slot is prevented or minimized. Rather, the pin rolls on the slot during operation, specifically on its mating contact surface (a lateral or longitudinal surface of the slot). This advantageously prevents wear due to sliding contact and thus increases the service life of the pin and the eccentric.In particular, the design of the pin with a non-circular profile, and at least the design of the involutes described here, also represent an independent invention. Assuming a movement range of + / - 10 degrees for the control weight, a module for such an involute toothing can be at least roughly determined: With a movement angle range of 20 degrees, 13 teeth (360 degrees divided by 20 degrees) would have to be present on a pitch circle that is determined by the distance between the center of gravity of the control weight and the axis of the shaft pin. The tooth module is the diameter of the pitch circle divided by the number of teeth. In the case of a movement angle range of "only" 10 degrees, the number of teeth would be 26. Suitable module numbers can therefore be chosen between the pitch circle diameter divided by 10 and divided by 30.

[0028] According to a preferred embodiment, the scroll machine has a counterweight that is connected to the drive shaft in a rotationally fixed manner, the center of gravity of which is arranged on the connecting line and which, together with the adjusting weight, forms a balancing weight for the second scroll. The counterweight is heavier than the adjusting weight, in particular so that the adjusting weight can be minimized. In particular, if the counterweight (its mass) is many times greater than the adjusting weight (its mass), any resulting imbalance can be kept low (or, in particular, neglected) when the adjusting weight is rotated about its pivot bearing and the center of gravity of the adjusting weight is shifted as a result. The counterweight that is connected in a rotationally fixed manner thus compensates for the "major portion" of the imbalance caused by the second scroll.

[0029] The scroll machine is preferably used as a scroll compressor. In this case, the delivery chambers represent compression chambers during intended (compressor) operation (as already indicated above), since their volume progressively decreases during operation. Likewise, the scroll machine described here and below can also be used in expander mode – particularly when the orbital direction is reversed – i.e., conveying from a high-pressure area to a low-pressure area. Especially in the case where the scroll machine is driven by an electric motor, generator mode is also possible, in which the scrolling movement is driven by the expansion of a medium in the delivery chambers.

[0030] During normal operation, only one of the two scrolls, in particular the second scroll, preferably orbits. In this case, the other scroll, specifically the first scroll, is preferably designed as a fixed scroll. For simplicity, the second scroll is referred to below as the orbiting scroll (also: "O-scroll").

[0031] For simplicity, the first scroll is also called a fixed scroll or “F-scroll.”

[0032] An embodiment of the invention is explained in more detail below with reference to a drawing. In the drawings: Fig. 1 shows a perspective view of a scroll machine according to the prior art, Fig. 2 shows a partial sectional view of a schematic longitudinal section of the scroll machine according to the prior art, Fig. 3 in a file view to Fig. 2 shows a detail and schematic view of a drive shaft of an electric motor drive of the scroll machine as well as a first and a second scroll of a compressor module of the scroll machine, Fig. 4 in a schematic diagram an arrangement of a radius compensation system relative to the drive shaft, Fig. 5 shows a perspective detailed view of a part of the radial compensation system of the scroll machine according to an embodiment of the invention, Fig. 6 shows a plan view of an end face of the drive shaft schematically another part of the radial compensation system, and Fig. 7 shows a further perspective detailed view of part of the radial compensation system from the rear.

[0033] Corresponding parts are always provided with the same reference symbols in all figures.

[0034] Fig. 1 shows a scroll machine according to the prior art. The scroll machine is installed, for example, as a scroll compressor 2, specifically as a refrigerant compressor, in a refrigerant circuit (not shown in detail) of an air conditioning system of a motor vehicle. The scroll compressor 2 is driven by an electric motor and, for this purpose, has an electric (electromotive) drive module 4 and a compressor module 6 coupled to it. A mechanical interface 8 is provided between the drive module 4 and the compressor module 6, by means of which the compressor module 6 is connected to the drive module 4 in terms of drive technology. The compressor module 6 is connected, specifically screwed, to the drive module 4 by means of flange connections 10 distributed around the circumference and extending in an axial direction A of the scroll compressor 2.

[0035] The drive module 4 has a drive housing 12 with an interior space 14 (see Fig. 2), the compressor module 6 comprises a compressor or "scroll housing 16" with a "scroll chamber 18". An electric motor 20 is arranged in the interior 14 as a drive. Fig. 1 The housing section of the drive housing 12 shown below encloses an electronics compartment 22 (see Fig. 2), in which motor electronics (not shown) controlling the electric motor 20 are arranged.

[0036] The scroll compressor 2 has a (refrigerant) inlet 24 (or connection) for connection to the refrigerant circuit and a (refrigerant) outlet 26. The inlet 24 is formed in an area of the drive housing 12 facing the electronics compartment 22. The outlet 26 is formed on a "bottom 28" of the scroll housing 16. When connected, the inlet 24 forms the low-pressure or suction side (suction gas side) and the outlet 22 forms the high-pressure or pump side (pump side) of the scroll compressor 2.

[0037] As from Fig. As can be seen in Figure 2, an "output-side" bearing plate 30 ("A" side, arranged in the direction of the downstream driven elements) is arranged in the area of the mechanical interface 8. This forms an intermediate wall, also referred to as a "center plate," between the drive module 4 and the compressor module 6.

[0038] As from Fig. 2, the compressor module 6 of the scroll compressor 2 has a first, fixed scroll (scroll part, hereinafter referred to as fixed scroll, "F-Scroll 32" for short) arranged in the scroll housing 16 and a second, movable scroll (scroll part, hereinafter referred to as orbiting scroll, "O-Scroll 34" for short). The O-Scroll 34 is coupled by means of a radius compensation system, hereinafter referred to as "swing link 36", to a (drive or motor) shaft 38 of the electric motor 20, which is guided in the bearing plate 30. The swing link 36 has an eccentric (or bearing journal 40) which is connected by means of a joining pin or shaft journal (here: "shaft pin 42"; see also Fig. 3) is connected to the shaft 38. The swing link 36 also has a control weight 44, which is eccentrically connected to the bearing journal 40 and the shaft 38 and which, together with a counterweight 46 connected to the shaft 38 in a rotationally fixed manner, forms a "balancing weight" or counterweight.

[0039] The bearing journal 40 is also mounted in a roller or ball bearing 48 held in the O-scroll 34. Another roller or ball bearing 50 is arranged in the bearing plate 30 to support the shaft 38. The O-scroll 34 is driven in an orbiting motion during operation of the scroll compressor 2 by means of the shaft 38 and the shaft pin 42 eccentrically mounted in the shaft 38. The F-scroll 32, on the other hand, is rigid, i.e., fixed to the scroll housing 16.

[0040] Both scrolls 32, 34 each have associated helical or spiral-shaped spiral walls 52, 54 (scroll walls, scroll spirals) that protrude axially from a respective base plate 56, 58. The F-scroll 32 additionally has a circumferential boundary wall 60. In the assembled state, the two scrolls 32 and 34 interlock with their spiral walls 52, 54. Between the scrolls 32, 34, i.e., between their spiral walls 50, 52 and the base plates 56, 58, (delivery or) compression chambers 62 are formed, the volume of which changes during operation of the electric motor 20.

[0041] A schematic layout of the Swing Links 36 is shown in Fig. 4. The core function of the swing link 36 is to maintain a sealing radial fit between the two scrolls 32, 34, even despite manufacturing tolerances, in particular the two spiral walls 52 and 54, which counteract such a fit.

[0042] As described above, the swing link 36 is coupled to the shaft 38 by means of the shaft pin 42. For this purpose, the swing link 36 has a bore 64 arranged eccentrically in the bearing journal 40. A journal center 66 of the bearing journal 40 (i.e., its bearing axis; or also: center of gravity of the O-scroll 34) and a pin center 68 (also: axis) of the shaft pin 42 (as well as the bore 64, i.e., its axis) are thus offset. A shaft center 70 of the shaft 38 (i.e., its axis) is also offset from the journal center 66 and the pin center 68.

[0043] The journal center 66 and the shaft axis 70 lie on a connecting line 72. This connecting line 72 separates an end face 74 of the shaft 38 into a first half-field 76 (in Fig. 4 left of the connecting line 72) and into a second half-field 78 (in Fig. 4 to the right of the connecting line 72). The shaft pin 42, at least its pin center 68, is arranged in the first half-field 76 and thus laterally offset from the connecting line 72. A direction of rotation of the drive shaft 38 in compression operation is oriented counterclockwise (when viewed as in Fig. 4 shown from both scrolls 32, 34 in the direction of the front surface 74).

[0044] The adjusting weight 44, or at least its center of gravity, is also arranged on the connecting line 72, at least in a designated rest position. Since the adjusting weight 44 also serves to rotate the bearing journal 40 around the shaft pin 42 during operation to compensate for the radius, the adjusting weight 44 is rotatable within a range of motion (angular range) of approximately + / - 10 degrees (relative to the journal center 66). Because the adjusting weight 44 is arranged on the connecting line 72 in the rest position, its centrifugal force also acts along the connecting line 72 and is thus diametrically opposite to the centrifugal force generated by the O-Scroll 34.

[0045] However, the actuating weight 44 is not rigidly connected and is directly connected (straight along the connecting line 72) to the bearing journal 40. In order to keep the mass of the actuating weight 44 as small as possible, thereby reducing any resulting imbalance when the actuating weight 44 is deflected, and yet still be able to exert a sufficiently large actuating force on the bearing journal 40, the actuating weight 44 is movably coupled to the bearing journal 40 by means of a lever arm 80 in an actuating bearing 82. In order to transmit the actuating force to the bearing journal 40, the lever arm 80 is also mounted in a stationary pivot bearing 84. The pivot bearing 84 thus forms a pivot point for the lever arm 80 and thus for the adjusting weight 44. The pivot bearing 84 is arranged in the second half-field 78, as is the adjusting bearing 82. In particular, the pivot bearing 84 is arranged in a quadrant opposite the shaft pin 42, which is diagonally opposite to the shaft axis 70.Preferably, the adjusting bearing 82 is also arranged in this quadrant. The quadrants are defined by the connecting line 72 and a dividing line perpendicular to this line, which runs through the shaft axis 70.

[0046] Furthermore, a straight line from the control weight 44 (specifically, its center of gravity) to the pivot bearing 86 (specifically, its bearing axis) is aligned perpendicular to a straight line between the pivot bearing 86 and the shaft pin axis 86 in the intended rest state. This results in advantageous force relationships.

[0047] In order to maximize the actuating force and, conversely, minimize the mass of the actuating weight 44, a distance Z between the bearing journal 40 and the connecting line 72 is smaller than a distance S between the actuating bearing 82 and the connecting line 72. Furthermore, a distance L (measured along the connection between the pivot bearing 84 and the actuating bearing 88) between the actuating bearing 82 and a perpendicular through the journal center 66 is greater than a distance P between this perpendicular and a parallel through the pin center 68. This results in the actuating bearing 82 being arranged as close to the edge of the bearing journal 40 as possible, in particular within the outer 30 percent of a radius of the bearing journal 40. This results in the actuating weight 44 exerting the greatest possible leverage on the bearing journal 40 with respect to the pin center 68.

[0048] The pivot bearing 84 is formed by a pin around which the lever arm 80 is rotatably coupled to the shaft 38. In the diagram shown, as well as in a variant not shown further, the adjusting bearing 82 is formed by a circular cylindrical pin 86, which is attached to the lever arm 80 and engages in a slot-like contour in the bearing pin 40, here an elongated hole 88. This allows the lever arm 80 to slide against the bearing pin 40 when rotated about the pivot bearing 84, thereby rotating the bearing pin 40 about the shaft pin 42.

[0049] To limit the rotation of the lever arm 80 and thus of the actuating weight 44 around the pivot bearing 84, the lever arm 80 is inserted into a recess 90 in the end face 74 of the shaft 38. This recess 90 is shaped in such a way that a rotation of the lever arm 80 of + / - 10 degrees around the pivot joint 84 is possible (see Fig. 6).

[0050] The Fig. The circular cylindrical pin 86 shown in Figure 4 is in accordance with a Fig. 5-7, the pin 92 is replaced by a pin with a polygonal profile. Instead of the elongated hole 88, the pin 92 is located in a longitudinal slot 96 that is open to the outside of the bearing journal 40. Specifically, the longitudinal slot 96 is formed in a collar-like extension 98 of the bearing journal 40 (see Fig. 5, Fig. 7). The pin 92 is rectangular, approximately square, with side surfaces 100 that are in contact with longitudinal surfaces 102 of the longitudinal slot 96 being curved outward. This allows for a larger contact area between the pin 92 and the longitudinal slot 96 than with a purely linear contact. This reduces (Hertzian) surface pressure, so that stress and wear in the adjusting bearing 82 can be reduced.

[0051] In an embodiment not shown in detail, the side surfaces 100 of the pin 92 are modeled as involutes of a rotational circle of the pin 92 around the pivot bearing 84, comparable to a tooth of a gear. The longitudinal surfaces 102 of the longitudinal slot 96 are also modeled as corresponding involutes—here, the rotational circle of the bearing journal 40 around the shaft pin 42. This allows the pin 92 and the corresponding longitudinal surface 102 of the slot 98 to roll against each other, similar to a gear pair, and a sliding component can be reduced or avoided. This can advantageously increase the service life of the pin 92 and the slot 98.

[0052] The subject matter of the invention is not limited to the exemplary embodiment described above. Rather, further embodiments of the invention can be derived by those skilled in the art from the above description. In particular, the individual features of the invention and their design variants described with reference to the exemplary embodiment can also be combined with one another in other ways. List of reference symbols 2 scroll compressors 4 Drive module 6 Compressor module 8 Interface 10 Flange connection 12 drive housing 14 Interior 16 scroll housings 18 scroll space 20 electric motor 22 Electronics room 24 Admission 26 Outlet 28 Floor 30 bearing plate 32 F-Scroll 34 O-Scroll 36 Swing Link 38 Wave 40 bearing journals 42 wave pin 44 Setting weight 46 Counterweight 48 ball bearings 50 ball bearings 52 Spiral wall 54 Spiral wall 56 Base plate 58 Base plate 60 boundary wall 62 Compressor chamber 64 bore 66 tenon center 68 Pin center 70 Wave center 72 connecting line 74 frontal area 76 half-field 78 half field 80 lever arm 82 parking bearings 84 pivot bearings 86 pin 88 slot 90 slot 92 pins 94 side area 96 Longitudinal slot 98 Extension 100 side area 102 Longitudinal surface A axial direction Z distance S distance L distance P distance QUOTES CONTAINED IN THE DESCRIPTION

[0000] This list of documents submitted by the applicant was generated automatically and is included solely for the convenience of the reader. This 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

[0000] DE 10 2012 104 045 A1

[0003]

Claims

[1] Scroll machine (2), in particular for refrigerant of a vehicle air conditioning system, comprising - a first scroll (32) having a first spiral wall (52) projecting in an axial direction (A), - a second scroll (34) with a second spiral wall (54) projecting in the axial direction (A), - a drive (20), - a drive shaft (38) by means of which the drive (20) and the second scroll (34) are coupled in terms of power transmission, and - a radius compensation system (36) which is connected between the drive shaft (38) and the second scroll (34) and which has an eccentric (40) which is coupled to the drive shaft (38) by means of a shaft pin (42) arranged eccentrically to the drive shaft (38) and to the second scroll (34) by means of a bearing pin (40) which is eccentric with respect to the shaft pin (42), wherein the shaft pin (42) is arranged in a first half-field (76) described by a connecting line (72) between a drive shaft axis (70) and a bearing axis (66) of the second scroll (34) with respect to an end face (74) of the drive shaft (38), wherein the radius compensation system (36) has a control weight (44) which is movably coupled to the eccentric (40) by means of a lever arm (80) in a control bearing (82), wherein the lever arm (80) is mounted in a stationary pivot bearing (84) which is arranged in a second half-field (78) separated from the first half-field (76) by the connecting line (72) on the end face (74) of the drive shaft (38), wherein the adjusting bearing (82) is arranged in the second half-field (78) with respect to the end face (74) of the drive shaft (38), and wherein a center of gravity of the adjusting weight (44) is arranged approximately on the connecting line (72). [2] Scroll machine (2) according to claim 1, wherein the rotary bearing (84) is arranged in a quadrant of the end face (74) opposite the shaft pin (42) via the drive shaft axis (70). [3] Scroll machine (2) according to claim 1 or 2, wherein the rotary bearing (84) is positioned such that approximately a right angle results between a straight line between a center of gravity of the actuating weight (44) and the rotary bearing (84) and a straight line between the rotary bearing (84) and the shaft pin axis (68). [4] Scroll machine (2) according to one of claims 1 to 3, wherein the rotary bearing (84) is arranged at the edge of the drive shaft (38), in particular with respect to a radius of the drive shaft (38) within the edge-side 50 percent, preferably 30 percent, of the radius. [5] Scroll machine (2) according to one of claims 1 to 4, wherein a distance between the adjusting bearing (82) and the shaft pin axis (68) is greater than the distance of the shaft pin axis (68) to the connecting line (72) of the second scroll (34). [6] Scroll machine (2) according to one of claims 1 to 5, wherein the lever arm (80) is received in the adjusting bearing (82) by means of a pin (86, 92) in a slot-like contour (88, 96) in the eccentric (40). [7] Scroll machine (2) according to claim 6, wherein the pin (92) has a non-circular profile. [8] Scroll machine (2) according to claim 7, wherein contact surfaces (100) of the pin (92) towards the eccentric (40) form flat convex curved sections of a profile approximating a polygon. [9] Scroll machine (2) according to claim 7 or 8, wherein contact surfaces (100) of the pin (92) towards the eccentric (40) are formed according to an involute of a rotation circle of the pin (92), and wherein corresponding counter-contact surfaces (102) of the slot-like contour (96) are formed according to a corresponding involute. [10] Scroll machine (2) according to one of claims 1 to 9, comprising a balancing weight (46) which is connected to the drive shaft (38) in a rotationally fixed manner, the center of gravity of which is arranged on the connecting line (72) and which, together with the adjusting weight (44), forms a balancing weight for the second scroll (34).

Images