DE102020211391A1 - Scroll compressor for vehicle air conditioning refrigerant - Google Patents

Abstract

The invention relates to a scroll compressor (2) for refrigerants in a vehicle air conditioning system, having a fixed scroll (32) with a base plate and a spiral wall (32a), a movable scroll (29) with a base plate (29b) and a spiral wall (29a). , which engages in the spiral wall (32a) of the fixed scroll (32) and forms compression chambers with it, and an anti-rotation mechanism (30, 30') for converting a rotational movement of a motor shaft (24) mounted in an end shield (8) into an orbiting movement of the movable scroll (29), wherein the anti-rotation mechanism (30, 30') has a support plate (34) which is coupled to the motor shaft (24), a shaft bolt (36) penetrating the support plate (34) being provided on whose opposite free ends, a first toothed rotor element (48) and a second toothed rotor element (50) are joined so that they are fixed to the shaft, the first rotor element (48) having a first Z ahnkontur (52, 52 ') of the bearing plate (8) is in meshing engagement, and wherein the second rotor element (50) with a second tooth contour (54, 54') of the base plate (29b) of the movable scroll (29) in a meshing intervention is.

Description

The invention is in the field of displacement machines based on the spiral principle and relates to a scroll compressor as an electric refrigerant drive, in particular as a refrigerant compressor for refrigerants in a vehicle air conditioning system.

Air conditioning systems are regularly installed in motor vehicles, which air-condition the vehicle interior with the aid of a system forming a refrigerant circuit. Such systems basically have a circuit in which a refrigerant is guided. The refrigerant, for example R-744 (carbon dioxide, CO ₂ ) or R-134a (1,1,1,2-tetrafluoroethane), is heated in an evaporator and compressed using a (refrigerant) compressor or compressor, with the refrigerant then emits the absorbed heat again via a heat exchanger before it is fed back to the evaporator via a throttle.

Scroll technology is often used as a refrigerant compressor to compress a refrigerant-oil mixture. Most of the resulting gas-oil mixture is separated, and the separated gas is fed into the air-conditioning circuit. If necessary, the separated oil can be fed to moving parts within the scroll compressor as a refrigerant compressor, suitably driven by an electric motor, for lubricating moving parts.

The structure and operation of such a scroll compressor for the refrigerant or the refrigerant-oil mixture of a motor vehicle air conditioning system is, for example, in DE 10 2012 104 045 A1 described. Essential components of such scroll compressors are two scroll parts (scrolls) that can be moved relative to one another.

The scroll parts are usually designed as a stationary, fixed scroll (fix scroll, displacement scroll) and as a movable, orbiting scroll (counter scroll, rotor scroll). The two scrolls have basically the same structure and each have a base plate (main body, scroll disk) and a spiral (snail-shaped) wall (spiral wall, scroll wall) extending in the axial direction from the base plate. In the assembled state, the spiral walls of the two scrolls are nested in one another and form several compression chambers between the scroll walls that touch one another in sections.

When the movable scroll orbits, the sucked-in gas-oil mixture travels via an inlet from a low-pressure chamber to a first, radially outer compression chamber (suction chamber) and from there via further compression chambers (compression chamber) to the radially innermost compression chamber (discharge chamber) and from there over a central outlet, for example in the form of a bore, and optionally two adjacent auxiliary valves, also in the form of bores in the base plate of the fixed scroll, into an outlet or high-pressure chamber. The chamber volume in the compression chambers decreases from radially outside to radially inside, and the pressure of the increasingly compressing medium increases. During operation of the scroll compressor, the pressure in the compressor chambers thus increases from radially outside to radially inside.

To drive the movable scroll, an electric motor is typically provided, the motor shaft of which is drivingly coupled to the movable scroll part by means of at least one (A-side) eccentric shaft journal.

An orbiting movement is to be understood here and in the following in particular as an eccentric, circular movement path in which the movable scroll itself does not rotate about its own axis. The orbiting movement of the movable scroll is brought about by means of an anti-rotation mechanism, which prevents the scroll from rotating and is mechanically coupled to the motor shaft.

Due to the manufacturing tolerances of both scroll contours to each other and other components that are involved in the so-called anti-rotation mechanism, the real eccentric track of the movable scroll usually deviates from an ideal eccentric track. The anti-rotation mechanism also enables forced radial contact by dividing the tangential force required for the drive, which is introduced via the swing link pivoted on the eccentric pin, into a tangential and radial component.

For the purpose of radial tolerance compensation of the eccentric track of the orbiting scroll, a balancing weight, also known as an eccentric or "swing link", is typically provided, which causes the (real) eccentric radius to be adapted to an ideal track during compressor operation. The counterweight thus ensures that the movable scroll constantly nestles against the fixed scroll.

The motor shaft is usually mounted by means of a bearing of an end shield (central plate, center plate), the anti-rotation mechanism often having a number of axial pins (pins) in addition to the counterweight, which are positively fixed in the end shield. The pins engage in circular, bead-like openings in the base plate of the movable scroll, and each form a so-called pin-ring contact. During compressor operation, the pins roll or roll off the circular port walls, preventing self-rotation. To reduce friction and improve the service life, for example, sliding rings are used in the openings.

For example, such anti-rotation mechanisms have six such pin-ring contacts. In this case, the pin-ring contacts are in particular arranged offset from one another by 60°, with one of the pin-ring contacts alternately experiencing the greatest mechanical load in the course of the orbiting movement.

The acoustics of the scroll compressor are adversely affected by these changing support contacts.

Anti-rotation mechanisms of this type therefore have a large number of components, as a result of which the assembly of the scroll compressor is comparatively complicated and expensive.

The invention is based on the object of specifying a particularly suitable scroll compressor. In particular, a scroll compressor with an improved anti-rotation mechanism is to be specified.

The object is achieved with the features of claim 1. Advantageous refinements and developments are the subject matter of the dependent claims.

The scroll compressor according to the invention is intended as a compressor for refrigerants of a vehicle air conditioning system and is suitable and set up for this.

The scroll compressor has a fixed scroll and a movable scroll, which means in the driven state - i.e. during operation (compressor operation) - orbiting (oscillating) scroll. The movable scroll is also referred to below as an orbiting scroll.

The scrolls or scroll parts each have a base plate (bottom plate) and a spiral wall (scroll spiral) extending essentially perpendicularly therefrom, with the particularly crescent-shaped compressor chambers being formed between the interlocking spiral walls of the two scrolls (scroll parts). The spiral walls of the scroll parts, which are preferably of essentially symmetrical design, each have a spiral angle of at least 720°, for example.

The scroll compressor has, for example, an electric or electromotive drive, which drives the movable scroll via a motor shaft (drive shaft). The motor shaft is rotatably mounted at least in sections in a bearing plate (hereinafter also referred to as center plate) between the drive and the scroll parts by means of a bearing. An anti-rotation mechanism is provided to convert the rotary motion of the motor shaft into the orbital motion of the movable scroll.

The anti-rotation mechanism according to the invention has a support plate which is coupled to the motor shaft. The support plate is penetrated by at least one shaft bolt, which is rotatably or rotatably mounted in the support plate. The shaft bolt protrudes from the carrier plate on both sides, with a first toothed rotor element and a second toothed rotor element being joined to the opposite free ends so that they are fixed to the shaft. In other words, the rotor elements are non-rotatably (torsionally rigid) or connected in parallel by means of the shaft bolt.

The rotor elements are each in meshing engagement with an associated tooth contour. A meshing engagement is to be understood here in particular as a form-fitting engagement of complementarily shaped tooth structures (toothing). The first tooth contour for the first rotor element is here arranged on the end shield, and the second tooth contour for the second rotor element is arranged on the base plate of the movable scroll.

In compressor operation, ie when the motor shaft rotates, the carrier plate is rotated, as a result of which the rotor elements roll or roll off on the respectively assigned tooth contour. This means that the orbiting scroll continuously, ie essentially without interruption, has positive contact with the fixed or stationary bearing plate during the orbiting movement. In other words, the orbiting scroll always has a positive connection to a non-rotating component or the end shield via the anti-rotation mechanism. This results in a particularly stable and smooth-running anti-rotation mechanism. As a result, the scroll compressor has improved acoustics, i.e. reduced noise emissions.

A "positive fit" or a "positive connection" between at least two parts connected to one another is understood here and in the following in particular to mean that the The parts connected to one another are held together at least in one direction by direct meshing of contours of the parts themselves or by indirect meshing via an additional connecting part. The "blocking" of a mutual movement in this direction is therefore due to the shape.

“Axial” or an “axial direction” is understood here and in the following in particular as a direction parallel (coaxial) to the axis of rotation of the drive, i.e. parallel to the motor shaft or perpendicular to the base plates of the scrolls. Correspondingly, here and below, “radial” or a “radial direction” means in particular a direction oriented perpendicular (transverse) to the axis of rotation of the drive along a radius of the drive or the scrolls. Here and in the following, “tangential” or a “tangential direction” means in particular a direction along the circumference of the drive (circumferential direction, azimuthal direction), ie a direction perpendicular to the axial direction and to the radial direction.

In an advantageous development, the at least one shaft bolt is arranged on the carrier plate parallel and at a radial distance from the motor shaft. In other words, the shaft bolt is oriented axially. As a result, a structurally simple and cost-reduced anti-rotation mechanism is formed.

During assembly, radial play is preferably compensated for between the rotor elements and the tooth contours, as a result of which continuous contact between the wall flanks of the orbiting scroll and those of the fixed scroll is made possible during operation. This minimizes leakage gaps and compensates for manufacturing tolerances. The connection between the motor shaft and the base plate is adapted in terms of structure, for example, in such a way that it can fulfill the same function as that of a counterweight. In a suitable embodiment, the at least one shaft bolt is positioned on the carrier plate in such a way that, together with the dead weight of the carrier plate, it counteracts the static unbalance of the movable scroll.

In an expedient development, a number of shaft bolts, ie at least two, preferably three, in particular four shaft bolts, are provided, each with a first and second rotor element, which are distributed on the carrier plate on the circumferential side. As a result, the forces acting during operation are distributed evenly over a number of tooth flanks, which advantageously reduces the demands on the mechanical properties of the rotor elements and/or tooth contours. It is thus conceivable, for example, to produce the rotor elements and/or tooth contours from a plastic material.

For the purpose of mechanical coupling, the motor shaft and the carrier plate are joined to one another, for example, in a form-fitting manner or in a form-fitting and force-fitting manner or with a material fit.

The conjunction “and/or” is to be understood here and in the following in such a way that the features linked by means of this conjunction can be designed both together and as alternatives to one another.

A “positive connection” or a “positive connection” between at least two parts connected to one another is understood here and in the following in particular to mean that the parts connected to one another are prevented from sliding off one another due to a frictional force acting between them. If there is no "connection force" that causes this frictional force (this means the force that presses the parts against each other, for example a screw force or the force of weight itself), the non-positive connection cannot be maintained and can therefore be released.

A "material connection" or a "material connection" between at least two parts connected to one another is understood here and in the following in particular to mean that the parts connected to one another are possibly under the effect at their contact surfaces through material union or crosslinking (e.g. due to atomic or molecular bonding forces). an additive are held together.

For example, the motor shaft and the support plate have interlocking contours; a threaded connection is also conceivable, for example, in which the motor shaft has an external thread that can be screwed into an internal thread of the support plate. Alternatively, for example, an interference fit between the motor shaft and the carrier plate is possible. Additionally or alternatively, for example, a welded connection between the motor shaft and the support plate is possible.

In a particularly stable and durable design, the motor shaft and the carrier plate are connected to one another in one piece, that is to say in one piece or monolithically. In other words, the motor shaft and the support plate are designed as a common component. This reduces the assembly work involved in manufacturing the scroll compressor.

Appropriately, the tooth contours are fixed to the end shield or the movable connected to the scroll. In one possible embodiment, the first tooth contour in particular is designed to be fixed or stationary. In other words, the first tooth contour is fixed to the end shield. This means that the first tooth contour essentially does not move during compressor operation.

In a preferred embodiment, the toothed components, that is to say the rotor elements and the tooth contours, each have helical teeth. This means that the teeth of the rotor elements are not arranged parallel to the axis of rotation or to the shaft bolt. Each of the rotor element-tooth contour pairs thus has a continuous transition into and out of mesh, as a result of which the transmission of the torque runs more smoothly. This means that there is continuous meshing between the tooth contours and the runner elements, improving the smoothness of the anti-rotation mechanism. This results in less noise during operation and thus improves the acoustics of the scroll compressor. When the motor shaft rotates, the movement is transferred to the carrier plate connected to the shaft. The movable scroll would now orbit and could also rotate around its eccentric bearing axis. At the same time, the first runner element also moves on its orbiting path and, thanks to its teeth, rolls off on the fixed first tooth contour. The two rotor elements rotate at the same speed due to their non-rotatable connection. In a particularly suitable development, a first rolling radius ratio of the first rotor element to the first tooth contour is the inverse of a second rolling radius ratio of the second rotor element to the second tooth contour, so that the movable scroll is prevented from rotating itself.

The tooth contours and runner elements are designed, for example, as gear wheels and/or as toothed belts. In one possible embodiment, the rotor elements are designed as gear wheels and the tooth contours as gear wheels and/or toothed belts. This ensures a particularly expedient and structurally simple configuration of the rotor elements and tooth contours. In order to implement a particularly noise-reduced anti-rotation mechanism, it is possible, for example, to design the or each tooth contour as an elastic toothed belt. The elasticity reduces or dampens the transmission of vibrations, further improving the acoustics of the scroll compressor.

The tooth contours are, for example, joined to the end shield or the base plate in a non-positive and/or positive manner by means of compression. An additional or further aspect of the invention provides that the first tooth contour is integrally formed (in one piece, monolithically) on the end shield and/or the second tooth contour is integrally formed on the base plate. This means that the or each tooth contour is milled from the solid, for example as part of the base plate or the end shield. This ensures a particularly high stability of the tooth contour. Furthermore, the number of components is reduced, which simplifies the assembly of the scroll compressor. It is also conceivable, for example, for the tooth contours to be molded onto the base plate or the bearing plate as injection molded parts.

The tooth contours and the rotor elements are designed, for example, with external teeth, ie, for example, as external gears. In a preferred embodiment, however, the runner elements are designed as internal runners, which engage in an internal toothing of the first and second tooth contour. This simplifies the storage of the movable scroll in the carrier plate, since no gearing is necessary in this area. Another advantage of this variant is that due to the larger rolling radii, the necessary supporting forces of the self-rotational moment of the movable scroll are lower, as a result of which an axial space saving is made possible. Thus, the stress on the teeth during operation is reduced, improving the robustness of the anti-rotation mechanism. In addition, due to the reduction in force, it is possible, for example, to implement the toothing of the rotor elements and/or tooth contours using a cost-effective material, such as a plastic material.

• 1 in perspektivischer Darstellung einen Scrollverdichter,
• 2 in perspektivischer Darstellung einen Antirotationsmechanismus des Scrollverdichters in einer ersten Ausführungsform,
• 3 in Schnittdarstellung den Antirotationsmechanismus,
• 4 in Draufsicht ausschnittsweise den Antirotationsmechanismus mit Blick auf einen beweglichen Scroll,
• 5 in Draufsicht ausschnittsweise den Antirotationsmechanismus mit Blick auf ein Lagerschild,
• 6 in perspektivischer Darstellung den Antirotationsmechanismus in einer zweiten Ausführungsform, und
• 7 in Schnittdarstellung den Antirotationsmechanismus.

Exemplary embodiments of the invention are explained in more detail below with reference to a drawing. Show in it:

• 1 a perspective view of a scroll compressor,
• 2 a perspective view of an anti-rotation mechanism of the scroll compressor in a first embodiment,
• 3 the anti-rotation mechanism in a sectional view,
• 4 top view of a detail of the anti-rotation mechanism with a view of a movable scroll,
• 5 top view of a detail of the anti-rotation mechanism with a view of an end shield,
• 6 a perspective view of the anti-rotation mechanism in a second embodiment, and
• 7 the anti-rotation mechanism in a sectional view.

Corresponding parts and sizes are always provided with the same reference symbols in all figures.

the 1 shows a scroll compressor 2 according to the invention, which is installed, for example, as a refrigerant compressor in a refrigerant circuit, not shown, of an air conditioning system of a motor vehicle. The electric motor scroll compressor 2 has an electric (electric motor) drive 4 and a compressor head 6 coupled to it. A bearing plate (center plate) 8 is provided as a mechanical interface between the drive 4 and the compressor head 6 , by means of which the compressor head 6 is connected to the drive 4 in terms of drive technology.

The bearing plate 8 forms an intermediate wall between a drive housing 10 and a compressor head housing 12. The compressor head 6 is connected (joined, screwed) to the drive 4 by means of flange connections 14 distributed on the circumference and extending in an axial direction A of the refrigerant drive 2, which are only shown in the figures are provided with reference symbols by way of example.

A housing section of the drive housing 10 on the compressor head side is designed as a motor housing for accommodating an electric motor, not shown in detail, and on the one hand through an integrated housing partition wall, not shown, to an electronics housing provided with a housing cover with motor electronics (electronics) 16 that control the electric motor, and on the other hand through the mechanical interface 8 closed. In the area of the electronics housing, the drive housing 10 has a connection section 18 for making electrical contact between the electronics 16 and an on-board network of the motor vehicle.

The scroll compressor 2 has a (refrigerant) inlet or (refrigerant) feed 20 for connection to the refrigerant circuit and a (refrigerant) outlet 22 . The inlet 20 is formed in an area of the motor housing that faces the electronics housing. The outlet 22 is formed on a bottom of a compressor head housing 12 . When connected, inlet 20 forms the low pressure or suction side (suction gas side) and outlet 22 forms the high pressure or pump side (pump side) of scroll compressor 2.

The in particular brushless electric motor has a rotor which is coupled in a torque-proof manner to a motor shaft 24 and which is arranged rotatably within a stator. The motor shaft 24 is rotatably or rotatably mounted in the drive housing 10 by means of two bearings. The bearing 26 on the compressor head side is accommodated in the bearing plate 8 and is designed, for example, as a ball bearing.

The bearing 26 is accommodated in a bearing seat 27 of the end shield 8 . A shaft seal 28 is arranged between the bottom of the bearing seat 27 and the bearing 26, by means of which the motor shaft 24 or the drive housing 10 is sealed.

The compressor head 6 has a movable scroll (scroll part) 29 arranged in the compressor housing 12 . This is coupled to the motor shaft 24 of the electric motor by means of an anti-rotation mechanism 30 . The movable scroll 29 is driven in an orbiting manner when the scroll compressor 6 is in operation.

The compressor head 6 also has a rigid scroll (scroll part) 32 , that is to say fixed in the compressor housing 12 in a fixed manner. The two scrolls (scroll parts) 29, 32 engage with their snail or spiral spiral walls (scroll walls, scroll spirals) 29a, 32a, which protrude axially from a respective base plate 29b, only the base plate 29b of the scroll 29 being shown in the figures. The spiral walls 29a, 32a are provided with reference numbers in the figures merely by way of example. The scroll 32 also has a circumferential boundary wall 32c forming the outer circumference.

During compressor operation, the motor shaft 24 is driven in rotation, with the rotational movement of the motor shaft 24 being converted into an orbiting movement of the scroll 29 by means of the anti-rotation mechanism 30 .

The following is based on the 2 until 5 a first embodiment of the anti-rotation mechanism 30 according to the invention is explained in more detail.

The anti-rotation mechanism 30 has a support plate 34 which is designed in one piece, that is to say in one piece or monolithically, with the motor shaft 24 . The carrier plate 34 is formed on the end face of the shaft end of the motor shaft 24 facing the base plate 29a. The carrier plate 34 has a substantially oval cross-sectional shape and is penetrated by an axial shaft bolt 36 which is rotatably or rotatably mounted in the carrier plate 34 .

On the side facing the scroll 29, the support plate 34 has a recess as a form-fitting receptacle for an extension 38 of the scroll 29, which is formed onto the base plate 28b so as to protrude axially. The extension 38 is designed as a bearing seat for a bearing 40, by means of which the base plate 29a is mounted so that it can rotate relative to the carrier plate 34 or the motor shaft 24. The bearing 40 is designed as a ball bearing, for example. The extension 38 is surrounded by an annular space or an annular groove 42 of the base plate 29b. The bearing plate 8 has a corresponding annular groove 44 which surrounds an annular collar 46 through which the motor shaft 24 passes.

The shaft bolt 36 protrudes axially over the support plate 34 on both sides, with a toothed rotor element 48, 50 being joined to the opposite free ends so as to be fixed to the shaft or fixed against rotation. In this embodiment, the rotor elements 48, 50 are designed as external gears, in particular with helical teeth.

The runner elements 48, 50 are each in a form-fitting meshing engagement with an associated tooth contour 52, 54. The tooth contour 52 for the runner element 48 is here on the bearing plate 8, and the tooth contour 54 for the runner element 50 is on the base plate 29b of the movable scroll 29 arranged. In this exemplary embodiment, the tooth contours 52, 54 are designed as external gears, in particular with helical teeth, which are placed on the annular collar 46 or on the extension 38.

The tooth contour 52 is held rigidly or fixedly on the ring collar 46 , the tooth contour 54 being rigidly fixed relative to the extension 38 or scroll 29 . The tooth contours 52, 54 are, for example, joined to the ring collar 46 or to the extension 38 in a non-positive and/or positive manner by means of pressing.

Because of the toothing, there is a form-fitting connection in the pairs of rotor elements and tooth contours, with a torsionally rigid connection between the rotor elements 48 , 50 being present.

In compressor operation, ie when the motor shaft 24 rotates, the carrier plate 34 is rotated. The tooth contour 52 is fixed, as a result of which the runner element 48 rolls or rolls on the toothed outer contour of the tooth contour 52 . The two runner elements 48, 50 rotate at the same speed due to their non-rotatable connection via the shaft bolt 36, so that the runner element 50 subsequently rolls or rolls on the toothed outer contour of the toothed contour 54. The rolling radius ratio of the rotor element 48 to the tooth contour 52 is the inverse of the rolling radius ratio of the rotor element 50 to the tooth contour 54, so that the movable scroll 29 is prevented from rotating itself. The tooth contour 54 or the scroll 29 thus performs only a translational orbiting movement without rotation during compressor operation.

Due to the anti-rotation mechanism 30 according to the invention, the orbiting scroll 29 is continuously, i.e. essentially without interruption, in form-fitting contact with the fixed or stationary bearing plate 8 during compressor operation. In other words, the orbiting scroll 29 always has a form-fitting connection to the non-rotating end shield 8 on.

The shaft bolt 36 is arranged parallel and radially spaced from the motor shaft 24 on the carrier plate 34 . In other words, the shaft bolt 36 is positioned at a radial distance dR from an axis of rotation D of the motor shaft 24 . The central axis of the extension 38 has a radial offset with respect to the axis of rotation D. Due to this radial distance, also referred to as eccentricity E, the extension 38 is positioned on the carrier plate 34 in such a way that it acts together with the carrier plate 34 against the static unbalance of the movable scroll 29 . The geometry and shape of the support plate 34 and its own weight are selected in such a way that the imbalance in the compressor operation is as minimal as possible. In a suitable dimensioning, the eccentricity has a value of 4.5 mm (millimeters), for example, and the distance dR has a value of at least 20 mm.

In an equally suitable dimensioning, the rolling radius ratio of the rotor element 48 to the tooth contour 52 is, for example, three to one (3:1), the rolling radius ratio of the rotor element 50 to the tooth contour 54 correspondingly being one to three (1:3). This results in an overall ratio of three to three (3:3) or one to one (1:1) transmission. Since the tooth contour 52 is fixed and therefore cannot rotate, the tooth contour 54 cannot rotate as a result either. As a result, the rotational movement of the tooth contours 52 and 54 is adapted to one another, as a result of which the scroll 29 is prevented from rotating of its own accord. The rolling radius ratios are preferably dimensioned as small as possible.

In the 4 and 5 an orbit 56 of the scrolling movement of the scroll 29 and an orbit 58 of the outer rotor movement of the rotor element 48 or 50 is shown as a dotted projection line. In one possible dimensioning, the orbit 56 has a diameter, for example of 9 mm and the orbit 58 has a diameter of about 40 mm.

Based on 6 and the 7 a second exemplary embodiment of the anti-rotation mechanism 30' according to the invention is explained in more detail below.

This embodiment of the anti-rotation mechanism 30′ essentially corresponds to the variant described above, with the tooth contours 52′, 54′ being designed as internal or ring gears, in which the rotor elements 48, 50 designed as external gears roll as internal rotors. The tooth contours 52', 54' are used here on the outer circumference of the respective annular groove 44 and 42, respectively. Suitably, the rotor elements 48, 50 and the tooth contours 52', 54' each have helical gearing.

As in the perspective view of 6 As can be seen comparatively clearly, the carrier plate 34 has a ramp 60 oriented obliquely to the axial direction A. The region of the support plate 34 in which the shaft bolt 36 is mounted is retracted axially by the ramp 60 . In other words, the area in which the shaft bolt 36 is not arranged is axially upstanding or raised, so that a bearing seat 62 for the bearing 40 is formed. This simplifies the assembly of the rotor element 50 and the bearing 40 . Furthermore, the (construction) weight is reduced and the balancing is improved.

The invention is not limited to the exemplary embodiments described above. On the contrary, other variants of the invention can also be derived from this by a person skilled in the art without departing from the subject matter of the invention. In particular, all of the individual features described in connection with the exemplary embodiments can also be combined with one another in other ways without departing from the subject matter of the invention.

For example, it is conceivable that the tooth contours 52, 52', 54, 54' and/or the runner elements 48, 50 are designed as elastic toothed belts. This reliably reduces or dampens oscillations and vibrations. Also conceivable is an embodiment of the rotor elements 48, 50 as bevel gears or bevel gears, in particular with helical gearing.

In another, not shown in detail, the tooth contours 52, 52', 54, 54' are not designed as separate components or gears, but are integral, i.e. one-piece or monolithic, introduced or molded into the material of the bearing plate 8 or the base plate 29b .

In addition or as an alternative, for example, a plurality of shaft bolts 36 are arranged on the carrier plate 34 .

Reference List

2

scroll compressor

4

drive

6

compressor head

8th

bearing shield

10

drive housing

12

compressor housing

14

flange connection

16

engine electronics

18

connector section

20

inlet

22

outlet

24

motor shaft

26

camp

27

bearing seat

28

shaft seal

29

Scroll

29a

spiral wall

29b

base plate

30, 30'

anti-rotation mechanism

32

Scroll

32a

spiral wall

32c

boundary wall

34

backing plate

36

shaft bolt

38

extension

40

camp

42

ring groove

44

ring groove

46

Gorget

48

runner element

50

runner element

52, 52"

tooth contour

54, 54"

tooth contour

56

orbit

58

orbit

60

ramp

62

bearing seat

A

axial direction

D

axis of rotation

dr

distance

E

eccentricity

QUOTES INCLUDED IN DESCRIPTION

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

Patent Literature Cited

• DE 102012104045 A1 [0004]

Claims (11)

Scroll compressor (2) for refrigerants of a vehicle air conditioning system, having - a fixed scroll (32) with a base plate and with a spiral wall (32a), - a movable scroll (29) with a base plate (29b) and with a spiral wall (29a) which engages with the spiral wall (32a) of the fixed scroll (32) and forms compression chambers with it, and - an anti-rotation mechanism (30, 30') for converting a rotational movement of a motor shaft (24) mounted in an end shield (8) into an orbiting movement of the movable scroll (29), - wherein the anti-rotation mechanism (30, 30') comprises a carrier plate (34) which is coupled to the motor shaft (24), - at least one shaft bolt (36) penetrating the carrier plate (34) being provided, at the opposite free ends of which a first toothed rotor element (48) and a second toothed rotor element (50) are joined so as to be fixed to the shaft, - wherein the first rotor element (48) is in meshing engagement with a first tooth contour (52, 52') of the bearing plate (8), and - wherein the second slider element (50) is in meshing engagement with a second tooth contour (54, 54') of the base plate (29b) of the movable scroll (29). Scroll compressor (2) after claim 1 , characterized in that the at least one shaft bolt (36) is arranged parallel and spaced radially from the motor shaft (24) on the support plate (34). Scroll compressor (2) after claim 1 or 2 , characterized in that the at least one shaft bolt (36) is positioned such that it counteracts the static imbalance of the movable scroll (29). Scroll compressor (2) after one of Claims 1 until 3 , characterized in that a number of shaft bolts (36) with first and second rotor elements (48, 50) are provided, which are arranged distributed on the support plate (34) on the circumferential side. Scroll compressor (2) after one of Claims 1 until 4 , characterized in that the motor shaft (24) and the support plate (34) are integrally connected to each other. Scroll compressor (2) after one of Claims 1 until 5 , characterized in that the first tooth contour (52, 52') is fixed. Scroll compressor (2) after one of Claims 1 until 6 , characterized in that the rotor elements (48, 50) and the tooth contours (52, 52', 54, 54') have a helical toothing. Scroll compressor (2) after one of Claims 1 until 7 , characterized in that a first rolling radius ratio of the first rotor element (48) to the first tooth contour (52, 52') is inverse to a second rolling radius ratio of the second rotor element (50) to the second tooth contour (54, 54'). Scroll compressor (2) after one of Claims 1 until 8th , characterized in that the runner elements (48, 50) are designed as gear wheels and the tooth contours (52, 52', 54, 54') as gear wheels and/or toothed belts. Scroll compressor (2) after one of Claims 1 until 9 , characterized in that the first tooth contour (52, 52') is integrally formed on the bearing plate (8) and/or the second tooth contour (54, 54') is integrally formed on the base plate (29b). Scroll compressor (2) after one of Claims 1 until 10 , characterized in that the rotor elements (48, 50) are designed as internal rotors which engage in an external toothing of the first and second tooth contour (52, 52', 54, 54').

Images