Compensating device for a scroll compressor

Abstract

The invention relates to a balancing device (36) for a scroll compressor (6), comprising a motor shaft (22) with an eccentrically arranged shaft journal (38) which projects axially upwards from a shaft end face (66), an eccentrically arranged eccentric bushing (40) on the shaft journal (38) for positive engagement with a bearing (46) of a movable scroll (34), a weight unit (42) for static balancing of the movable scroll (34), which is rotatably arranged about the shaft end face (36), and a spring element (76) for mechanically preloading the weight unit (42), wherein the spring element (76) is fixed at least partially to the shaft end face (66), and wherein the spring element (76) bears against a restoring force against a contact surface (84) of the weight unit (42), and a preload force (K) directed tangentially to the motor shaft (22) is applied to the exerts weight unit (42).

Description

[0001] The invention relates to a balancing device for a scroll compressor, for converting a rotational movement of a motor shaft into an orbiting movement of a movable scroll or compressor part. The invention further relates to a scroll compressor with such a balancing device.

[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, carbon dioxide (CO2), 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] Scroll technology is often used as a refrigerant compressor to compress a refrigerant-oil mixture. The resulting gas-oil mixture is largely separated, with the separated gas being introduced into the air conditioning circuit, while the separated oil can, if necessary, be fed into the scroll compressor for lubrication, cooling, and sealing of moving parts.

[0004] The design and operation of such a scroll compressor for the refrigerant or refrigerant-oil mixture of a motor vehicle air conditioning system is described, for example, in DE 10 2012 104 045 A1. Essential components of such scroll compressors are two scroll parts that can move relative to each other.

[0005] 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 disc) 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 compression chambers between the scroll walls, which touch each other in sections.

[0006] An orbiting movement, here and in the following, is understood to mean, in particular, an eccentric, circular movement path in which the moving scroll itself does not rotate around its own axis. Thus, the scrolls always maintain a minimal distance from each other, with each orbiting movement forming essentially crescent-shaped compression chambers between the spiral walls, whose volume is progressively reduced or compressed during the movement (compression process).

[0007] To drive the movable scroll, an electric motor is typically provided, the motor shaft of which is drive-coupled to the movable scroll part by means of at least one (A-side) eccentric shaft journal (so-called eccentric or driver pin).

[0008] Due to the manufacturing tolerances of the movable scroll and other components involved in the so-called anti-rotation mechanism, the actual eccentric track of the movable scroll usually deviates from an ideal eccentric track.

[0009] For the purpose of radial tolerance compensation of the eccentric raceway of the orbiting scroll, a compensating device, also called eccentric or "swing link", is typically provided, which is intended to adjust the (real) eccentric radius to an ideal raceway during compressor operation.

[0010] Depending on the existing tolerance conditions, the compensation device, for example, causes the movable scroll spring to snug against the stationary scroll spring. This provides a certain degree of flexibility in the anti-rotation mechanism, which is also desirable due to manufacturing tolerances.

[0011] The balancing device serves primarily to statically balance the orbiting scroll, reducing centrifugal forces and scroll vibrations. For this purpose, the balancing device must have a certain minimum weight as unbalance. The balancing device is therefore typically made of a high-density material.

[0012] Due to an inhomogeneous torque curve during the compression cycle, a reaction can occur on the balance weight, resulting in relative movement of the balancer to the shaft journal. In particular, this results in a tangential back-and-forth movement of the balancer. This can cause a permanent change or shift in the balance weight's center of gravity during compressor operation, which can lead to acoustic NVH (noise, vibration, harshness) problems in the scroll compressor.

[0013] The invention is based on the object of providing a particularly suitable balancing device for a scroll compressor. In particular, a balancing device is to be provided that is improved with regard to NVH behavior during compressor operation. The invention is further based on the object of providing a particularly suitable scroll compressor.

[0014] With regard to the balancing device, the object is achieved according to the invention with the features of claim 1, and with regard to the scroll compressor with the features of claim 11. Advantageous embodiments and further developments are the subject of the dependent claims. The advantages and embodiments cited with regard to the balancing device are also transferable mutatis mutandis to the scroll compressor, and vice versa.

[0015] The balancing device according to the invention is intended for, and is suitable and configured for, a scroll compressor. The balancing device is designed in particular as a "swing link" and is, for example, part of an anti-rotation mechanism.

[0016] The balancing device comprises a motor shaft (drive shaft) with an eccentrically arranged drive pin as the eccentric shaft, which protrudes axially from a shaft end face. When installed, the shaft end faces a movable scroll (orbiting scroll) of the scroll compressor.

[0017] "Axial" or an "axial direction" is understood here and below to mean, in particular, a direction parallel (coaxial) to the motor shaft, i.e., perpendicular to the shaft end faces. Accordingly, "radial" or a "radial direction" is understood here and below to mean, in particular, a direction oriented perpendicular (transverse) to the motor shaft along a radius of the motor shaft. "Tangential" or a "tangential direction" is understood here and below to mean, in particular, a direction along the circumference of the motor shaft (circumferential direction, azimuthal direction), i.e., a direction perpendicular to the axial direction and the radial direction.

[0018] An eccentric bushing is mounted eccentrically on the shaft journal. The cylindrical eccentric bushing is positioned eccentrically with respect to both the drive shaft and the shaft journal. In other words, the shaft journal engages eccentrically with the eccentric bushing. The eccentric bushing is preferably rotatably mounted on the shaft journal. When installed, the eccentric bushing engages positively with a bearing of the movable scroll.

[0019] The weight unit is intended for, and is suitable and configured for, the static balancing of an orbiting scroll, i.e., for reducing centrifugal forces and vibrations during compression operation of the scroll compressor. The weight unit is arranged so as to be rotatable or rotatable around the shaft end face, in particular around the shaft journal, wherein the weight unit is preferably joined to the eccentric bushing. In particular, the weight unit is connected to the eccentric bushing in a rotationally fixed manner. For example, the weight unit and the eccentric bushing are designed as a single-piece, i.e., one-piece or monolithic, component.

[0020] The weight unit includes, for example, a joining plate for coupling to the eccentric bushing and a counterweight. The counterweight is arranged radially on the outside of the motor shaft and has a tangentially curved profile.

[0021] According to the invention, the compensating device comprises a spring element for mechanically preloading the weight unit. The spring element is arranged essentially between the shaft end face and the weight unit, in particular the counterweight.

[0022] A "spring element" here and below refers in particular to a spring-elastic or flexurally elastic element that, due to its elasticity, generates an opposing restoring force upon deflection. The spring element can be designed, for example, as an elastomer or as a mechanical spring (coil spring, torsion spring, leaf spring, etc.) or similar.

[0023] The spring element is fixed, at least in sections, to the shaft end face. The spring element also bears against a contact surface of the weight unit, counteracting a restoring force (spring force), and exerts a preload force or preload torque directed tangentially to the motor shaft on the weight unit, in particular on the counterweight. In other words, the weight unit is spring-elastically preloaded along the tangential direction.

[0024] The preload force or preload torque is preferably oriented along a closing direction. The closing direction here is understood to be the direction of rotation along which the (tangential) sealing between the compression chambers of the scroll parts occurs during the orbiting scrolling movement. In particular, the preload force is dimensioned such that contact between the orbiting and stationary scrolls is always guaranteed. Due to the preload force, radial and / or tangential lifting of the orbiting scroll is essentially impossible. This prevents or at least reduces unexpected movement of the orbiting scroll in the opening direction during normal operation. The mechanical preload of the spring element therefore also preloads the scroll walls relative to one another, so that, for example, less leakage occurs between the compression chambers at low speeds.

[0025] Preferably, the force of the spring element is introduced as close as possible to the shaft journal to ensure that the weight unit tilts as little as possible.

[0026] The spring element creates a particularly suitable balancing device or swing link. In particular, the preload force or preload torque counteracts unwanted back-and-forth movement of the balancing weight during compressor operation. This results in less rattling noise when the scroll compressor starts up. This results in a balancing device with improved NVH behavior.

[0027] In an advantageous development, the spring element has a fixed end fixed or attached to the shaft end face, a spring section that can be pivoted elastically or resiliently, and a free end that bears against the weight unit. The spring section, designed, for example, as a spring leg, is guided at least in sections around an outer circumference of the shaft end face and is arranged to be pivotable about a bearing point on the shaft end face. The bearing point is part of the shaft end face or its outer circumference and is designed, for example, as an approximately radially directed projection or corner region. The free end of the spring element or spring section bears against a contact surface of the weight unit, counter to a restoring force (spring force), and exerts a preload force or preload torque directed tangentially to the motor shaft on the weight unit, in particular on the counterweight.In other words, the weight unit is spring-elastically prestressed along the tangential direction.

[0028] In a preferred embodiment, the shaft end face has an axial notch that exposes a shoulder. The shaft journal is arranged on the end face of the shoulder, with the spring element arranged along the axial side surfaces or the outer circumference of the shoulder. This results in a particularly space-saving or compact balancing device, in which the spring element is arranged "nested" between the shoulder and the weight unit, in particular the balancing weight.

[0029] Here and in the following, a "notch" refers specifically to a recess or relief of a specific depth that opens toward the outer circumference or edge of the workpiece. The notch is thus a type of axial step at the end of the motor shaft.

[0030] In one conceivable embodiment, the notch is approximately crescent-shaped in a section plane oriented parallel to the shaft end face. The shoulder thus has an approximately three-quarter moon-shaped cross-section in the section plane. The bearing point is formed in particular at one of the two corner areas.

[0031] In an alternative embodiment, it is conceivable, for example, that instead of a notch, a slot-like, axial groove or recess is introduced into the front side of the shaft end, in which the spring element is seated at least in sections.

[0032] Preferably, the notch or groove is introduced into the shaft end by a milling process.

[0033] In a practical embodiment, the spring element, in particular the free end of the spring element, is designed to be cranked, with the free end resting on the contact surface at an apex. The cranking or bending creates a quasi-linear contact between the apex and the contact surface, thereby enabling more effective force introduction into the weight unit. Preferably, the free end has an approximately S-shaped cranking or bending, with the apex of the first S-bend resting on the contact surface, and the apex of the second S-bend forming a mechanical stop for limiting the movement of the spring leg. The counter-bearing of the stop is, for example, the outer circumference of the shaft end face, in particular a corner region of the three-quarter moon-shaped shoulder.

[0034] In a suitable refinement, the free end and the bearing point are arranged on diametrically opposite sides of the motor shaft or the shoulder. This creates a particularly long spring leg, increasing the torque for preloading the weight unit.

[0035] In a conceivable embodiment, the shaft end face or its outer circumference has a radially and / or tangentially oriented receiving slot for the positive and / or non-positive reception of the fixed end.

[0036] The conjunction “and / or” is to be understood here and in the following in such a way that the features linked by this conjunction can be formed both together and as alternatives to one another.

[0037] A "positive connection" or a "positive connection" between at least two interconnected parts is understood here and below in particular to mean that the interconnected parts are held together at least in one direction by a direct interlocking of the contours of the parts themselves or by an indirect interlocking via an additional connecting part. The "blocking" of mutual movement in this direction is therefore due to the shape.

[0038] A "positive connection" or a "positive connection" between at least two interconnected parts is understood here and below in particular to mean that the interconnected parts are prevented from sliding against each other due to a frictional force acting between them. If a "connecting force" causing this frictional force (this means the force that presses the parts against each other, for example, a screw force or the force of gravity itself) is missing, the positive connection cannot be maintained and can therefore be released.

[0039] In an equally conceivable alternative embodiment, the spring element, in particular the fixed end, engages behind the outer circumference of the shaft end face in a form-fitting and / or force-fitting manner, at least in sections. This means that the fixed end is held on the outer circumference of the shaft end face itself. Preferably, the outer circumference has a radially upstanding contour, edge, or corner region, which can be engaged behind by the fixed end, in particular in a form-fitting manner, tangentially.

[0040] In an advantageous embodiment, the spring element or the fixed end is arranged at the bearing point. In other words, the pivot axis for the spring section is located essentially in the area of ​​the fixed end. This results in a particularly material-saving spring element.

[0041] In one possible embodiment, the spring element or the fixed end is guided tangentially around the shaft end face or its outer circumference. The shaft end face, in particular the shoulder, is thus encompassed by the fixed end. This eliminates the need for radial machining of the motor shaft, simplifying the production of the compensation device.

[0042] The spring element is designed, for example, as a helical, spiral, or torsion spring. In a preferred embodiment, the spring element is designed, in particular, as a leaf spring. This results in a particularly compact spring element. Alternatively, the spring element can also be designed as an elastomer.

[0043] The scroll compressor according to the invention is designed in particular as an electric or electromotive refrigerant compressor for a vehicle air conditioning system. The scroll compressor comprises a compensating device as described above. This results in a particularly suitable, quiet-running, and NVH-improved scroll compressor.

[0044] Exemplary embodiments of the invention are explained in more detail below with reference to a drawing. In the drawings: Fig. 1 in sectional view an electric refrigerant drive, Fig. 2 shows a perspective view of a compensation device in a first embodiment, Fig. 3 in perspective view the balancing device without a weight unit, Fig. 4 in perspective view the weight unit of the balancing device, Fig. 5 shows a perspective view of the compensation device in a second embodiment, and Fig. 6 shows a perspective view of the compensation device in a third embodiment.

[0045] Corresponding parts and sizes are always provided with the same reference symbols in all figures.

[0046] The Fig. 1 depicts a refrigerant drive 2, in particular a refrigerant compressor. The refrigerant drive 2, also referred to below as the refrigerant compressor, is installed, for example, in a refrigerant circuit (not shown in detail) of a motor vehicle's air conditioning system.

[0047] The refrigerant compressor 2, which is in particular electric or electromotive, has an electric (electromotive) drive 4 and a scroll compressor 6 coupled to the drive as the compressor head. The scroll compressor 6 is also referred to below as compressor 6 for short.

[0048] The drive 4 on the one hand and the compressor 6 on the other hand are designed modularly, for example, so that, for example, a drive 4 can be coupled to different compressors 6. A transition area formed between the modules 4 and 6 has a mechanical interface in the form of a center plate 8 designed as a bearing plate. The compressor 6 is connected to the drive 4 via the center plate 8.

[0049] The drive 4 has a pot-shaped drive housing 10 with two housing sections 10a and 10b, which are separated from each other in a fluid-tight manner by a monolithically integrated housing partition (bulkhead) 10c within the drive housing 10. The drive housing 10 is preferably manufactured as a die-cast part from an aluminum material.

[0050] The compressor-side housing section is designed as a motor housing 10a for accommodating an electric motor 12. The motor housing 10a is closed on one side by the (housing) intermediate wall 10c and on the other side by the central plate 8. The housing section opposite the intermediate wall 10c is designed as an electronics housing 10b, in which power electronics (motor electronics) are housed, not shown in detail, which controls and / or regulates the operation of the electric motor 12—and thus of the compressor 6.

[0051] The electronics housing 10b is closed with a housing cover (electronics cover) 14 toward a front side of the drive 4 facing away from the compressor 6. When the housing cover 14 is open, the power electronics is mounted in an electronics compartment 16 formed by the electronics housing 10b and is still easily accessible for maintenance or repair purposes when the housing cover 14 is removed.

[0052] The drive housing 10 has a (suction gas) inlet or suction port (inlet) (not shown in detail) for connection to the refrigerant circuit of the air conditioning system, approximately at the level of the electric motor 12. A fluid, in particular a suction gas, flows into the drive housing 10, in particular into the motor housing 10a, via the inlet. From the motor housing 10a, the fluid flows through the central plate 8 to the compressor 6. The refrigerant is then compressed by the compressor 6 and exits the refrigerant circuit of the air conditioning system at a bottom-side (refrigerant) outlet 18 (outlet) of the compressor 6.

[0053] The outlet 18 is formed on the bottom of a pot-shaped compressor housing 20 of the compressor 6. When connected, the inlet forms the low-pressure or suction side, and the outlet 18 forms the high-pressure or pump side, of the refrigerant compressor 2.

[0054] The brushless electric motor 12, in particular, comprises a rotor 24 that is non-rotatably coupled to a motor shaft 22 and rotatably arranged within a stator 26. The motor shaft 22 is rotatably or rotatably mounted by means of two bearings 28. One bearing 28 is arranged in a bearing seat 30 that is integrally formed on the housing base or on the intermediate wall 10c of the drive housing 10. The other bearing 28 is received in the central plate 8. The central plate 8 has a sealing ring 32 for sealing against the motor shaft 22.

[0055] The scroll compressor 6 has a movable scroll (scroll part) 34 arranged in the compressor housing 20. This scroll is coupled to the motor shaft 22 of the electric motor 12 by means of a compensating device 36, acting as a swing link or eccentric, via a shaft journal 38. The shaft journal 38 is designed as a so-called eccentric or drive pin and is arranged eccentrically to the motor shaft 22.

[0056] The shaft journal 38 is, for example, designed as a single piece, i.e., integral or monolithic, with the motor shaft 22; alternatively, the shaft journal 38 can also be pressed into a bore of the motor shaft 22 as a joining pin.

[0057] The balancing device 36 has an eccentric bushing 40 eccentrically mounted on the shaft journal 38 and a weight unit 42, for example, integrally formed therewith, with a balancing weight 44. The eccentric bushing 40 is mounted in a bearing 46 held in the movable scroll 34. The movable scroll 34 is driven in an orbiting motion during operation of the scroll compressor 6.

[0058] The scroll compressor 6 also has a rigid, fixed scroll (scroll part) 48, which is fixedly mounted in the compressor housing 20. The two scrolls (scroll parts) 34, 48 mesh with each other via their helical or spiral-shaped spiral walls (scroll walls, scroll spirals), which protrude axially from a respective base plate. The scroll 48 also has a circumferential boundary wall forming the outer circumference.

[0059] The scrolls 34, 48 are connected to the motor compartment of the motor housing 10a via a suction or low-pressure chamber 50 of the compressor housing 20. During compressor operation, the fluid is pumped from the low-pressure chamber 50 to a high-pressure chamber 52 of the compressor housing 20.

[0060] To lubricate the bearings 28, 46, a lubricant or oil (e.g., PAG or POE) is added to the refrigerant within the refrigerant compressor 2. The fluid flow delivered by the compressor 6 is thus a mixture of the gaseous refrigerant and the liquid, droplet-like oil. The oil is separated by an oil separator 54 and returned via a return line or oil return to lubricate moving parts.

[0061] Between the scroll 48 and the high-pressure chamber 52, i.e., at the bottom of the base plate, a flutter valve (finger spring valve) 56 is arranged as a covering or closing part, with which a central, high-pressure-side outlet opening 58 of the scroll part 48 is covered. A flutter valve 56 is understood here, in particular, to be a check valve which, without any other external drive, opens in the flow direction solely due to pressure differences on the two valve sides and closes again automatically, thus covering the outlet opening 58.

[0062] The outlet opening 58 is also referred to below as the main outlet port. Radially spaced from the main outlet port 58, two additional outlet openings, known as pre-outlets, can be provided. These outlet openings are also referred to below as secondary valve ports.

[0063] The reed valve 56 serves both as a main valve for the main outlet port 58 and as a pre- or auxiliary outlet valve for the secondary valve ports of the scroll member 48, preventing overcompression of the fluid during compressor operation. This ensures pressure-regulated fluid discharge from the outlet ports 58.

[0064] Between the A-side bearing plate 8 (central plate) and the movable scroll 34 is a backpressure chamber as part of an unspecified backpressure system, in which the compensating device 36 is housed. The backpressure chamber is defined in the compressor housing 20 by the base plate of the movable scroll 34. The backpressure chamber extends partially into the base plate of the movable scroll 40 and is sealed from the base plate by a seal 60.

[0065] “Axial” or an “axial direction A” is understood here and below to mean, in particular, a direction parallel (coaxial) to the axis of rotation of the electric motor 12, i.e., along the longitudinal direction of the motor shaft 22. Correspondingly, “radial” or a “radial direction R” is understood here and below to mean, in particular, a direction oriented perpendicular (transverse) to the axis of rotation of the electric motor 12 along a radius of the electric motor 12 or the motor shaft 22. “Tangential” or a “tangential direction T” is understood here and below to mean, in particular, a direction along the circumference of the electric motor (circumferential direction, azimuthal direction) 12 or the motor shaft 22, i.e., a direction perpendicular to the axial direction and the radial direction.

[0066] The structure of the compensation device 36 is shown below using the Fig. 2 to Fig. 4. The compensating device 36 is, in particular, part of an unspecified anti-rotation device, which prevents the scroll 34 from rotating and is mechanically coupled to the motor shaft 22. The anti-rotation device enables forced radial adjustment by dividing the tangential force required for the drive, which is introduced via the weight unit 42 rotatably mounted on the shaft journal 38, into a tangential and radial component.

[0067] In addition to the compensating device, the anti-rotation device comprises a number of axial pins 62, which are, for example, non-positively fixed in a stationary central plate 8. In the illustrated embodiment, six pins 62 are provided, for example. The pins 62 engage in circular, bead-like openings or recesses (not shown in detail) in the base plate of the movable scroll 34, each forming a so-called pin-ring contact. During compressor operation, the pins 62 roll or roll against the circular opening walls, thereby preventing the movable scroll 34 from rotating on its own.

[0068] The motor shaft 22 has a shaft end face 66 facing the scroll 34, which forms the shaft-end section of the motor shaft 22. The shaft end face 66 has a guide 68 formed by an axial groove in the shaft end face 66 or the shaft end. The guide 68 thus divides the shaft end face 66 into two island-like end faces 70a, 70b. The end face 70b is approximately crescent-shaped in cross-section.

[0069] The end face 70a has a circumferential, axially oriented side surface, which is referred to below as the outer circumference 72 of the end face 70a. The outer circumference 72, or the cross-sectional shape of the end face 70a, has two opposite corner regions 73a, 73b. The approximately bolt-shaped or cylindrical shaft journal 38 is arranged axially upright on the end face 70a.

[0070] The eccentric bushing 40 is mounted eccentrically on the shaft journal 38, which is arranged eccentrically to the motor shaft rotation axis. The eccentric bushing 40 is thus arranged eccentrically with respect to both the motor shaft 22 and the shaft journal 38. The eccentric bushing 40 is preferably rotatably mounted on the shaft journal 38, with the eccentric bushing 40 positively engaging the bearing 46 of the movable scroll 34 when installed.

[0071] The Fig. The weight unit 42 shown individually in Figure 4 is intended for the static balancing of the orbiting scroll 34, i.e., for reducing centrifugal forces and vibrations during compression operation of the scroll compressor 6, and is suitable and configured for this purpose. The weight unit 42 is arranged rotatably or rotatably around the shaft end face 66, in particular around the shaft journal 38, wherein the weight unit 42 is preferably joined to the eccentric bushing 40. In particular, the weight unit 42 and the eccentric bushing 40 are designed as a one-piece, i.e., one-piece or monolithic, component.

[0072] The weight unit 42 has, for example, a joining plate 74 for coupling to the eccentric bushing 40, and the balancing weight 44 arranged radially on the outside.

[0073] The compensating device 36 further comprises a spring element 76 for mechanically preloading the weight unit 42. In this exemplary embodiment, the spring element 76 is designed, in particular, as a leaf spring.

[0074] The spring element 76 has a fixed end 78 ( Fig. 3), a flexible or resiliently pivotable spring leg as spring section 80, and a free end 82 which rests against the weight unit 42 at least in sections.

[0075] The spring section 80 is seated in the guide 68, so that the axial side walls of the guide 68 limit or restrict the pivoting path of the spring section 80.

[0076] The spring leg 80, which is curved toward the counterweight 44 or the end face 70b, is guided at least partially around the outer circumference 72 of the end face 70a and is pivotably mounted about a bearing point on the shaft end face 36. The bearing point is formed in particular by the corner region 73a around which the spring leg 80 is placed.

[0077] The embodiment of the Fig. 2 and Fig. Figure 3 shows a spring element 76 in which the fixed end 78 is guided around the outer circumference 72 of the end face 70a. The fixed end 78 engages in a form-fitting manner behind the corner region 73b, where the stop for the apex 88 is formed. For example, the outer circumference 72 has a corresponding notch for holding the fixed end 78.

[0078] The free end 82 of the spring element 76 or of the spring leg 80 rests against a restoring force (spring force) on an approximately radially oriented contact surface 84 of the weight unit 42 and exerts a preload force K directed tangentially to the motor shaft 22 or - due to the rotatable mounting of the weight unit 42 - a preload torque D on the weight unit 42, in particular on the counterweight 44. In other words, the weight unit 42 is elastically preloaded along the tangential direction T. The preload force K and the preload torque D are in the Fig. 2 is shown schematically with arrows. Preferably, the preload force K or the preload torque D is oriented along a closing direction of the movable scroll 34.

[0079] The free end 82 of the spring element 76 is designed as a crank. The free end 82 has an approximately S-shaped bend or bend, with an apex 86 of the first S-bend resting against the contact surface 84, and an apex 88 of the second S-bend forming a mechanical stop for limiting the spring leg movement. The counterbearing of the stop or apex 88 is, for example, the corner region 73b of the shoulder 68.

[0080] Below, based on the Fig. 5 and Fig. 6 two further embodiments of the compensating device 36 are explained in more detail. In the embodiments of Fig. 5 and Fig. 6, the eccentric bushing 40 and the weight unit 42 are not shown.

[0081] In the embodiment of the Fig. 5, the shaft end face 66 has a shoulder 90 which is exposed by an axial notch of the shaft end face 66 or the shaft end.

[0082] The notch has an approximately crescent-shaped cross-sectional shape, so that the circular cross-section of the motor shaft 22 is reduced to an approximately three-quarter moon-shaped cross-section of the shoulder 68.

[0083] The shoulder 90 has a frontal end face 70 and a circumferential, axially oriented side surface, which in this embodiment form the outer circumference 72 of the shaft end face 66 or the shoulder 90. The outer circumference 72, or the cross-sectional shape of the shoulder 90, has the opposite corner regions 73a, 73b. The approximately bolt-shaped or cylindrical shaft journal 38 is arranged axially upwardly on the end face 70.

[0084] In the Fig. In the embodiment shown in Figure 5, the spring section 80 or the fixed end 78 is not guided to the corner region 73b, but only around the corner region 73a. A radially and / or tangentially oriented receiving slot (not shown in detail) is formed in the outer circumference 72, in which the fixed end 78 is seated in a form-fitting and / or force-fitting manner.

[0085] The embodiment of the Fig. 6 shows a spring element 76 in which the fixed end 78 is guided around the outer circumference 72. The fixed end 78 engages in a form-fitting manner behind the corner region 73b, where the stop for the apex 88 is formed. Alternatively, a receiving slot can be provided at the corner region 73b, into which the fixed end 78 is inserted.

[0086] The claimed invention is not limited to the exemplary embodiments described above. Rather, other variants of the invention can also be derived therefrom by those skilled in the art within the scope of the disclosed claims without departing from the subject matter of the claimed invention. In particular, all individual features described in connection with the various exemplary embodiments can also be combined in other ways within the scope of the disclosed claims without departing from the subject matter of the claimed invention.

[0087] Instead of a leaf spring, a spiral or torsion spring, or an elastomer can be used as spring element 76. List of reference symbols 2 refrigerant drive / compressor 4 Drive 6 scroll compressors, compressors 8 Central plate 10 drive housing 10a Motor housing 10b Electronics housing 10c Housing partition 12 electric motor 14 Housing cover 16 Electronics compartment 18 Outlet 20 compressor housing 22 Motor shaft 24 rotors 26 Stator 28 warehouses 30 bearing seat 32 Sealing ring 34 Scroll 36 Compensation device 38 shaft journals 40 eccentric bushing 42 weight unit 44 Counterweight 46 warehouses 48 Scroll 50 low-pressure chamber 52 High pressure chamber 54 oil separators 56 Flapping valve 58 Outlet opening 60 Sealing 62 pen 66 Shaft end face 68 leadership 70, 70a, 70b front face 72 Outer circumference, side surfaces 73a Corner area, storage location 73b Corner area, counter bearing 74 Joining plate 76 spring element 78 Festival End 80 spring section / spring leg 82 freelancers 84 contact surface 86, 88 vertex 90 paragraph A axial direction R Radial direction T Tangential direction K Preload force D Preload torque 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

[0004]

Claims

[1] Compensation device (36) for a scroll compressor (6), comprising - a motor shaft (22) with an eccentrically arranged shaft journal (38) which projects axially upwards from a shaft end face (66), - an eccentric bushing (40) arranged eccentrically on the shaft journal (38) for positive engagement in a bearing (46) of a movable scroll (34), - a weight unit (42) for static balancing of the movable scroll (34), which is arranged rotatably around the shaft end face (36), and - a spring element (76) for mechanically preloading the weight unit (42), - wherein the spring element (76) is fixed at least in sections to the shaft end face (66), and - wherein the spring element (76) bears against a restoring force against a contact surface (84) of the weight unit (42) and exerts a pretensioning force (K) directed tangentially to the motor shaft (22) on the weight unit (42). [2] Compensating device (36) according to claim 1, characterized by , - that the spring element (76) has a fixed end (78) fixed to the shaft end face (66), - that the spring element (76) has a spring section (80) which is guided at least in sections around the shaft end face (66) and which is arranged pivotably about a bearing point (73a) on the shaft end face (66), and - that a free end (82) of the spring section (80) bears against the contact surface (84) of the weight unit (42) against the restoring force and exerts the pretensioning force (K) directed tangentially to the motor shaft (22) on the weight unit (42). [3] Compensating device (36) according to claim 1 or 2, characterized bythat the shaft end face (66) has an axial notch which exposes a shoulder (90), on the end face (70) of which the shaft journal (38) is arranged, wherein the spring element (76) is arranged along the axial side surfaces (74) of the shoulder (90). [4] Compensating device (36) according to claim 2 or 3, characterized by that the free end (82) of the spring element (80) is cranked and rests against the contact surface (84) at an apex point (86). [5] Compensating device (36) according to one of claims 2 to 4, characterized by that the free end (82) and the bearing point (73a) are arranged on diametrically opposite sides of the motor shaft (22). [6] Compensating device (36) according to one of claims 1 to 4, characterized by that the shaft end face (66) has a receiving slot for the positive and / or non-positive reception of the spring element (76). [7] Compensating device (36) according to one of claims 1 to 6, characterized by that the spring element (76) engages behind an outer circumference (72) of the shaft end face (66) in a form-fitting and / or force-fitting manner, at least in sections. [8] Compensating device (36) according to one of claims 2 to 7, characterized by that the fixed end (78) is arranged at the bearing point (73a). [9] Compensating device (36) according to one of claims 2 to 8, characterized by that the fixed end (78) is guided tangentially around the shaft end face (66). [10] Compensating device (36) according to one of claims 1 to 9, characterized by that the spring element (76) is designed as a leaf spring. [11] Scroll compressor (6) for a vehicle air conditioning system, comprising a compensating device (36) according to one of claims 1 to 10.

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