DE102022132456A1 - Scroll compressor - Google Patents

Abstract

The invention relates to a spiral compressor (156) with at least one spiral-shaped stator blade (6, 86, 114) attached or formed on an inner end wall (84, 112) of a compressor housing (158) and at least one spiral-shaped displacer blade (12, 90, 118) attached or formed on a displacement disk (8, 88`, 116`), wherein the stator blade (6, 86, 114) and the displacement blade axially engage with one another and delimit sickle-shaped pressure chambers (14a, 14b, 16a, 16b) between them, wherein the displacement disk is rotatably mounted on an eccentric pin (20, 74, 76) of a drive shaft (18, 72) and, when the drive shaft (18, 72) rotates, is guided by means of a guide device (22, 166, 178) in a translational orbital motion. It is provided that the guide device has a guide lever (24, 168, 180) and a support lever (30, 174, 186), that the guide lever (24, 168, 180) is radially aligned with respect to the hub axis (10, 108, 136) of the displacement disk (8, 88', 116') and is rigidly attached to the displacement disk (8, 88', 116') with its inner end (26, 170, 182), that the support lever (30, 174, 186) has spring-elastic properties, and that the support lever is tangentially aligned with respect to the hub axis (10, 108, 136) of the displacement disk (8, 88', 116') between the outer end (28, 172, 184) of the guide lever (24, 168, 180) and the compressor housing (4, 158) and is firmly connected to both of them.

Description

The invention relates to a spiral compressor, with at least one spiral-shaped stator blade fastened or formed on an inner end wall of a compressor housing and at least one spiral-shaped displacer blade fastened or formed on a displacer disk, wherein the stator blade and the displacer blade axially interlock and delimit sickle-shaped pressure chambers between each other, wherein the displacer disk is rotatably mounted on an eccentric pin of a drive shaft and is guided in a translatory orbital movement by means of a guide device when the drive shaft rotates.

Spiral compressors, also known as scroll compressors, are preferably used in stationary and mobile cooling units, in heat pumps and also in combustion engines to increase their boost pressure. A spiral compressor has at least one spiral stator blade fixed to the housing and one movably arranged spiral displacement blade, which delimit several sickle-shaped pressure chambers between them. The stator blade is attached to an inner end wall of a compressor housing. The displacement blade, on the other hand, is arranged on a displacement disk, which is rotatably mounted on an eccentric pin of a drive shaft. When the drive shaft is rotating, i.e. driven by a drive motor, the displacement disk with the displacement blade should perform a translatory orbital movement to achieve a high level of efficiency, i.e. be deflected radially in accordance with the circumferential displacement of the eccentric pin. However, the displacement blade should largely retain its circumferential orientation, i.e. not pivot around its own hub axis if possible. If this is ensured, the blades can be designed and arranged in such a way that the displacement blade approaches the stator blade in places to within a few micrometers. This means that the pressure chambers, which are displaced circumferentially in the direction of rotation of the drive shaft and radially from the outside to the inside while reducing their volume, are relatively well sealed when the drive shaft rotates. However, to ensure the translatory orbital movement of the displacement disk, a guide device is required, which can be designed in different ways.

In one of the DE 33 13 000 A1 In the known spiral compressor, the guide device is designed as a guide gear with a guide shaft and a toothed belt drive. The guide shaft is rotatably mounted in a compressor housing near the outer circumference of the displacement disk via two roller bearings. At the end facing the displacement disk, the guide shaft is provided with an eccentric pin which has the same eccentricity as the eccentric pin of the drive shaft. The eccentric pin of the guide shaft is rotatably mounted in an axial guide bore of the displacement disk by means of a roller bearing. The guide shaft is in drive connection with the drive shaft via the toothed belt drive. If the eccentric pin of the drive shaft and the guide shaft have the same circumferential orientation, the guide gear ensures precise guidance of the displacement disk in a translatory orbital movement when the drive shaft is rotating. The disadvantages of such a guide gear, however, are the high design effort, the large installation space required and the high drive torque required for the guide shaft.

In the DE 34 07 939 C1 A spiral compressor is described in which the guide device is formed by a crank arm which is arranged tangentially on the outer circumference of the displacement disk in the extension of a displacement blade. The crank arm is articulated at both ends, i.e. on the outside of the compressor housing and on the inside of the displacement disk. When the drive shaft rotates, the crank arm is alternately deflected radially outwards or inwards around its outer bearing, which causes the displacement disk to pivot periodically in the circumferential direction. The compact design of this known guide device is offset by the disadvantages of the crank arm bearing being subject to wear and the reduced efficiency of the spiral compressor due to the pivoting of the displacement disk.

In the EN 10 2013 218 430 A1 In the known spiral compressor, the guide device comprises an outer ring body fixed to the housing with a cylindrical inner wall, an inner ring body with a cylindrical outer wall arranged coaxially within this outer ring body and connected to the displacement disk, and several conical thrust levers with cylindrical heads and spherical feet. In the inner wall of the outer ring body, several cylindrical recesses are formed distributed around the circumference, which are aligned parallel to the axis of the drive axis. In the outer wall of the inner ring body, the same number of radial guide openings are formed distributed around the circumference. The thrust levers are pivotably mounted with their heads in the recesses of the outer ring body and with their feet are guided radially displaceably and pivotably in the guide openings of the inner ring body. This known guide device The guide device requires a relatively large installation space and requires a lot of assembly work to complete. In addition, the guide device is subject to wear due to the frictional contact of the many thrust levers with the inner walls of the recesses and the guide openings and requires an intensive supply of lubricant to the contact areas.

In view of the disadvantages of the known guide devices of scroll compressors, the object of the invention is to present a scroll compressor with a guide device that is simply constructed, takes up little installation space and is as wear-free as possible.

This object is achieved by a scroll compressor having the features of claim 1. Advantageous further developments are defined in the dependent claims.

Accordingly, the invention relates to a spiral compressor with at least one spiral stator blade attached or formed on an inner end wall of a compressor housing and at least one spiral displacer blade attached or formed on a displacement disk, wherein the stator blade and the displacement blade axially interlock and delimit sickle-shaped pressure chambers between each other, wherein the displacement disk is rotatably mounted on an eccentric pin of a drive shaft and is guided in a translatory orbital movement by means of a guide device when the drive shaft rotates.

To achieve the stated object, this scroll compressor is provided with the guide device having a guide lever and a support lever, the guide lever being radially aligned with respect to the hub axis of the displacer disk and being rigidly attached to the displacer disk with its inner end, the support lever having spring-elastic properties, and the support lever being arranged with a tangential alignment with respect to the hub axis of the displacer disk between the outer end of the guide lever and the compressor housing and being firmly connected to both.

With the guide lever attached radially to the displacement disk and the elastic support lever arranged between the guide lever and the compressor housing, this guide device has a relatively simple structure, few components and requires little installation space. It also functions smoothly and wear-free. When the drive shaft rotates, the guide lever is deflected radially inward in accordance with the deflection by the rotating eccentric pin of the drive shaft and transfers this deflection radially outward to the support lever, which at least partially absorbs this movement through spring-elastic bending, stretching and compression. Since this is not completely possible, this results in a periodic pivoting movement of the displacement disk around the hub axis, but this only amounts to a few degrees. The pivoting movement of the displacement disk is smaller the longer the guide lever and the more elastic the support lever are. The guide lever is therefore preferably designed to be as long as possible, which is not a major problem insofar as its circumferential arrangement can be chosen as desired.

The support lever can be made of rubber or another spring-elastic material. Alternatively, the support lever can have at least one section which is made of a spring-elastic material and therefore has spring-elastic properties. Since the elasticity of rubber decreases significantly at temperatures below freezing, an elastomeric plastic which does not have this property is preferable for the support lever.

The support lever or the elastic portion of the support lever may have a circular cross-section.

However, it is also possible that the support lever or the elastic section of the support lever has an elliptical cross-section and, in order to achieve a lower bending stiffness in the radial direction, is arranged such that the smaller diameter of the elliptical cross-section of the support lever is aligned in the longitudinal direction of the guide lever.

As an alternative to rounded cross-sections, the support lever or the elastic section of the support lever can also have a square cross-section and, in order to achieve a lower bending stiffness in the radial direction, can be arranged such that two opposite parallel outer sides of the square cross-section are aligned in the longitudinal direction of the guide lever.

Alternatively, it is also possible for the support lever or the elastic portion of the support lever to have a cuboid-shaped cross-section and, in order to achieve a lower bending stiffness in the radial direction, to be arranged such that the smaller thickness of the cuboid-shaped cross-section is aligned in the longitudinal direction of the guide lever.

Irrespective of its cross-sectional shape, the support lever or the elastic section of the support lever can also have a constriction aligned in the longitudinal direction of the guide lever. Such a constriction acts as an elastic hinge and thus further reduces the flexural rigidity of the support lever or the elastic section in the radial direction.

The support lever can be rigidly attached to the guide lever and/or the compressor housing. This can be achieved, for example, by molding the support lever onto a fitting of the guide lever and/or the compressor housing by means of vulcanization or injection molding.

As an alternative to a design made of rubber or another elastomeric plastic, the support lever can also consist of a spring plate, for example made of spring steel, which is curved radially outwards or inwards in an arc shape to enable bending, stretching and compression with respect to the hub axis of the displacement disk.

All of the above types of support levers can also be attached to a fitting on the guide lever and/or the compressor housing using a bolt connection, i.e. a screw, rivet or split pin connection. In a support lever design using rubber or another elastomeric plastic, it is provided with at least one vulcanized or molded fitting on the end.

However, the support lever can also be hinged to the guide lever and/or the compressor housing.

For this purpose, the support lever can be pivotably mounted on a central cylindrical bearing pin of the guide lever at the end with a through opening that is cylindrical in the middle and widened in a V-shape on both sides, wherein the bearing pin is aligned axially parallel to the hub axis of the displacement disk.

Alternatively, however, it is also possible for the support lever, which for this purpose can be provided with at least one vulcanized or overmolded fitting at the end, to be pivotably mounted with at least one end-side bearing axis in a bearing bush that is aligned axially parallel to the hub axis of the displacement disk and rigidly attached to the guide lever and/or the compressor housing.

The design according to the invention can also be implemented in a two-stage spiral compressor, which has a first compressor stage and a second compressor stage. The two compressor stages each have a spiral-shaped stator blade attached or formed to an inner end wall of a compressor housing and a spiral-shaped displacer blade attached or formed to a displacement disk. The respective stator blade and the displacement blade associated with it engage axially with one another and delimit sickle-shaped pressure chambers between them. The two displacement disks are rotatably mounted on an eccentric pin of a common drive shaft at opposite ends of the compressor housing and are guided in a translatory orbital movement by means of a guide device when the drive shaft rotates. According to the invention, the at least one guide device has a guide lever and a support lever according to the type described.

• 1 einen Spiralverdichter mit einer erfindungsgemäßen Führungseinrichtung in einer ersten Funktionsstellung in einer vereinfachten Axialansicht,
• 1a den Spiralverdichter gemäß 1 in einer zweiten Funktionsstellung in einer vereinfachten Axialansicht,
• 1b den Spiralverdichter gemäß den 1 und 1a in einer dritten Funktionsstellung in einer vereinfachten Axialansicht,
• 1c den Spiralverdichter gemäß den 1 bis 1 b in einer vierten Funktionsstellung in einer vereinfachten Axialansicht,
• 2 eine erste Ausführungsform einer Führungseinrichtung eines Spiralverdichters in einer ausschnittweisen Axialansicht,
• 2a die Führungseinrichtung in einer Querschnittansicht A-A gemäß 2,
• 3 eine zweite Ausführungsform einer Führungseinrichtung eines Spiralverdichters in einer ausschnittweisen Axialansicht,
• 3a die Führungseinrichtung in einer Querschnittansicht B-B gemäß 3,
• 4 eine dritte Ausführungsform einer Führungseinrichtung eines Spiralverdichters in einer ausschnittweisen Axialansicht,
• 4a die Führungseinrichtung in einer Querschnittansicht C-C gemäß 4,
• 5 eine vierte Ausführungsform einer Führungseinrichtung eines Spiralverdichters in einer ausschnittweisen Axialansicht,
• 5a die Führungseinrichtung in einer Querschnittansicht D-D gemäß 5,
• 6 eine fünfte Ausführungsform einer Führungseinrichtung eines Spiralverdichters in einer ausschnittweisen Axialansicht,
• 7 eine sechste Ausführungsform einer Führungseinrichtung eines Spiralverdichters in einer ausschnittweisen Axialansicht,
• 8 eine siebte Ausführungsform einer Führungseinrichtung eines Spiralverdichters in einer ausschnittweisen Axialansicht,
• 9 eine achte Ausführungsform einer Führungseinrichtung eines Spiralverdichters in einer ausschnittweisen Axialansicht,
• 10 eine neunte Ausführungsform einer Führungseinrichtung eines Spiralverdichters in einer ausschnittweisen Axialansicht,
• 11 einen zweistufigen Spiralverdichter mit bekannten Führungseinrichtungen in einem schematischen Längsmittenschnitt, und
• 12 den zweistufigen Spiralverdichter gemäß 11 mit erfindungsgemäßen Führungseinrichtungen in einem Längsmittenschnitt.

The invention is explained in more detail below with reference to several embodiments shown in the accompanying drawing. The drawing shows

• 1 a scroll compressor with a guide device according to the invention in a first functional position in a simplified axial view,
• 1a the scroll compressor according to 1 in a second functional position in a simplified axial view,
• 1b the scroll compressor according to the 1 and 1a in a third functional position in a simplified axial view,
• 1c the scroll compressor according to the 1 to 1b in a fourth functional position in a simplified axial view,
• 2 a first embodiment of a guide device of a scroll compressor in a partial axial view,
• 2a the guide device in a cross-sectional view AA according to 2 ,
• 3 a second embodiment of a guide device of a scroll compressor in a partial axial view,
• 3a the guide device in a cross-sectional view BB according to 3 ,
• 4 a third embodiment of a guide device of a scroll compressor in a partial axial view,
• 4a the guide device in a cross-sectional view CC according to 4 ,
• 5 a fourth embodiment of a guide device of a scroll compressor in a partial axial view,
• 5a the guide device in a cross-sectional view DD according to 5 ,
• 6 a fifth embodiment of a guide device of a scroll compressor in a partial axial view,
• 7 a sixth embodiment of a guide device of a scroll compressor in a partial axial view,
• 8th a seventh embodiment of a guide device of a scroll compressor in a partial axial view,
• 9 an eighth embodiment of a guide device of a scroll compressor in a partial axial view,
• 10 a ninth embodiment of a guide device of a scroll compressor in a partial axial view,
• 11 a two-stage scroll compressor with known guide devices in a schematic longitudinal section, and
• 12 the two-stage scroll compressor according to 11 with guide devices according to the invention in a longitudinal center section.

In the simplified axial view according to 1 a spiral compressor 2 is shown, which has a spiral-shaped stator blade 6 attached to an inner end wall (not shown) of a compressor housing 4 and a spiral-shaped displacer blade 12 arranged on a displacement disk 8. The stator blade 6 and the displacer blade 12 engage axially and delimit four sickle-shaped pressure chambers 14a, 14b, 16a, 16b. The displacement disk 8 is rotatably mounted on an eccentric pin 20 of a drive shaft 18 and is guided in a translatory orbital movement by means of a guide device 22 when the drive shaft 18 rotates.

The guide device 22 comprises a guide lever 24 and a support lever 30. The guide lever 24 is aligned radially with respect to the hub axis 10 of the displacement disk 8 and is rigidly attached to the displacement disk 8 with its radially inner end 26. The support lever 30 is arranged with respect to the hub axis 10 of the displacement disk 8 with a tangential alignment between the radially outer end 28 of the guide lever 24 and the compressor housing 4 and is firmly connected to both of them. The support lever 30 also has spring-elastic properties.

In the 1 the scroll compressor 2 is in a first functional position in which the eccentric pin 20 of the drive shaft 18 is in a 270° position. In this functional position, the radially outer pressure chambers 14a, 14b are connected to a 1 not visible inlet chamber of the spiral compressor 2, while the radially inner pressure chambers 16a, 16b are completely closed. Due to the deflection of the displacement disk 8 by means of the eccentric pin 20, the support lever 30 is slightly compressed in a spring-elastic manner in the 270° position and bent towards the displacement disk 8. In addition, the displacement disk 8 carried out a slight pivoting movement of less than one degree clockwise compared to a fictitious neutral position which the guide device 22 would assume if the eccentric pin 20 were arranged centrally on the drive shaft 18.

In the 1 a In the illustration shown, the drive shaft 18 is compared to the 1 rotated 90° clockwise. The spiral compressor 2 is in a second functional position in which the eccentric pin 20 of the drive shaft 18 is in the 0° position. In this functional position, the radially outer pressure chambers 14a, 14b are significantly enlarged and have taken in air or another gas from the aforementioned inlet chamber of the spiral compressor 2. The radially inner pressure chambers 16a, 16b are still closed, but have further compressed the enclosed gas by reducing their volumes. Due to the vertical deflection of the displacer disk 8 by means of the eccentric pin 20 upwards or radially outwards, the support lever 30 was elastically stretched and bent away from the displacer disk 8 at one end. In addition, the displacer disk 8 performed a pivoting movement of two to three degrees clockwise in relation to the fictitious neutral position.

In the 1 b The drive shaft 18 is compared to the one in the 1a shown situation has been rotated clockwise by 90°, and the spiral compressor 2 is in a third functional position, in which the eccentric pin 20 of the drive shaft 18 is in a 90° position. In this functional position, the radially outer pressure chambers 14a, 14b are separated from the inlet chamber of the spiral compressor 2 and have smaller volumes while compressing the enclosed gas. The radially inner pressure chambers 16a, 16b have further reduced volumes and a first smaller connection to a radially inner and in the 1b not visible outlet space of the spiral compressor 2. Due to the described deflection of the displacement disk 8 by means of the eccentric pin 20, the support lever 30 was bent away from the drive shaft 18 and slightly stretched in a spring-elastic manner. In addition, the displacement disk 8 performed a slight pivoting movement of less than one degree in relation to the fictitious neutral position.

According to the presentation of the 1c The drive shaft 18 is compared to the 1b rotated a further 90° clockwise, and the spiral compressor 2 is therefore in a third functional position, in which the eccentric pin 20 of the drive shaft 18 is in a 180° position. In this functional position, the radially outer pressure chambers 14a, 14b are significantly reduced in size and have further compressed the gas trapped there. The radially inner pressure chambers 16a, 16b are now completely connected to the outlet chamber of the spiral compressor 2 (not visible here) and have almost completely pushed the previously trapped gas out into the outlet chamber. Due to the vertical deflection of the displacement disk 8 downwards by means of the eccentric pin 20, the support lever 30 was elastically compressed and bent downwards. In addition, the displacement disk 8 performed a larger pivoting movement of two to three degrees in relation to the fictitious neutral position.

The following are based on the 2 to 10 Several possible embodiments of the support lever 30 are explained.

In the partial axial view of the 2 and the cross-sectional view of the 2a according to the section plane AA of the 2 In a first embodiment, the support lever 30.1 consists of rubber or another elastomeric plastic and has a circular cross-section.

In the partial axial view of the 3 and the cross-sectional view of the 3a according to the cutting plane BB of the 3 In a second embodiment, the support lever 30.2 is also made of rubber or another elastomeric plastic, but it has an elliptical cross-section. In order to achieve a lower spring stiffness in the radial direction with respect to the hub axis 10 of the displacement disk 8, this support lever 30.2 is arranged such that the smaller diameter d of its elliptical cross-section is aligned in the longitudinal direction of the guide lever 24.

In the partial axial view of the 4 and the cross-sectional view of the 4a according to the cutting plane CC of the 4 In a third embodiment, the support lever 30.3 is also made of rubber or another elastomeric plastic, but now has a square cross-section. In order to achieve a lower spring stiffness in the radial direction with respect to the hub axis 10 of the displacement disk 8, the support lever 30.3 is arranged such that two opposite parallel outer sides 36, 36' of its square cross-sectional area are aligned in the longitudinal direction of the guide lever 24.

In the partial axial view of the 5 and the cross-sectional view of the 5a according to the cutting plane DD of the 5 In a fourth embodiment, the support lever 30.4 is also made of rubber or another elastomeric plastic, but it has a cuboid-shaped cross-section. In order to achieve a lower spring stiffness in the radial direction with respect to the hub axis 10 of the displacement disk 8, this support lever 30.4 is arranged such that the smaller thickness t of the cuboid-shaped cross-sectional area is aligned in the longitudinal direction of the guide lever 24.

In the partial axial view of the 6 In a fifth embodiment, the support lever 30.5 made of rubber or another elastomeric plastic has a constriction 38 aligned in the longitudinal direction of the support lever 30.5. Such a constriction 38 acts as an elastic folding hinge and thereby reduces the flexural rigidity of the support lever 30.5 in the radial direction.

The support levers 30.1, 30.2, 30.3, 30.4, 30.5 presented so far can be rigidly attached to the guide lever 24 and/or the compressor housing 4 and for this purpose can be molded onto a fitting of the guide lever 24 and/or the compressor housing 4 by means of vulcanization or injection molding.

In an alternative mounting method, the support lever 30.6 is to be mounted in accordance with the 7 In the sixth embodiment shown, the guide lever 24 is fastened to a fitting 42 of the guide lever 24 by means of a vulcanized or molded-in first fitting 40 via a bolt connection 44. This bolt connection 44 is formed, for example, by a rivet 46 inserted into holes in the two fittings 40, 42.

In the partial axial view of the 8th In a seventh embodiment, the support lever 30.7 made of rubber or another elastomeric plastic is positively pivotably mounted on a central cylindrical bearing pin 50 of the guide lever 24 by means of a centrally cylindrical and externally V-shaped through opening 48, wherein the bearing pin 50 is aligned axially parallel to the hub axis 10 of the displacement disk 8.

According to an alternative eighth embodiment, a partial axial view of the 9 The support lever 30.8 shown, made of rubber or another elastomeric plastic, can be pivoted by means of an end-side bearing axis 52 attached to the support lever 30.8 in a direction rigidly attached to the guide lever 24 and aligned axially parallel to the hub axis 10 of the displacement disk 8. The bearing shaft 52 of the support lever 30.8 can be part of a fitting vulcanized or molded into the end of the support lever 30.8.

In the partial axial view of the 10 According to a ninth embodiment, the support lever 30.9 consists of a spring plate which is curved radially outwards in an arc shape to enable it to be bent, stretched and compressed with respect to the hub axis 10 of the displacement disk 8. The support lever 30.9 is hereby analogous to the sixth embodiment of the support lever 30.6 according to 7 via a bolt connection 44 to a fitting 42 of the guide lever 24, wherein the bolt connection 44 is formed by a rivet 46 inserted into bores in the support lever 30.9 and the fitting 42.

The 11 shows schematically a longitudinal center section through a known two-stage scroll compressor 56, which has a compressor housing 58, an electric motor 66, a drive shaft 72, a first compressor stage 82 designed as a scroll compressor and a second compressor stage 110 designed as a scroll compressor.

The multi-part compressor housing 58 consists of a largely hollow cylindrical central housing 60 and two pot-shaped side housings 62, 64 arranged on both sides of it. The drive shaft 72 is rotatably mounted in the central housing 60 via two roller bearings 78, 80 arranged at the ends and designed as deep groove ball bearings. The electric motor 66 has a stator 68 and a rotor 70 arranged coaxially within the stator 68 and is arranged axially centrally between the two aforementioned roller bearings 78, 80. While the stator 68 is arranged in a rotationally fixed and axially fixed manner on the central housing 60, the rotor 70 is rigidly attached to the drive shaft 72.

The first compressor stage 82 is arranged in the first side housing 62. For this purpose, at least one first spiral-shaped stator blade 86 is formed on an inner end wall 84 of the first side housing 62. At least one first displacement blade 90 axially engaging with this first stator blade 86 is formed on a first displacement disk 88. This first displacement disk 88 is rotatably mounted on an axially adjacent first eccentric pin 74 of the drive shaft 72 via a third roller bearing 92 designed as a cylindrical roller bearing. To guide the first displacement disk 88 when the drive shaft 72 is rotating in a translational orbital movement, a known guide device 94 is provided, which comprises a first guide shaft 96 with a third eccentric pin 98 arranged on the outer circumference of the first displacement disk 88.

The eccentricity of the third eccentric pin 98 of the first guide shaft 96 is identical to that of the first eccentric pin 74 on the drive shaft 72. The main shaft of this guide shaft 96 is rotatably mounted in a first bearing bore 102 of the central housing 60 via two rolling bearings 100 designed as angular contact ball bearings, while the eccentric pin 98 of the first guide shaft 96 is rotatably mounted in a bearing bore 106 of the first displacement disk 88 via two rolling bearings 104 designed as angular contact ball bearings.

When the drive shaft 72 rotates, i.e. is driven by the electric motor 66, the first guide shaft 96 should rotate synchronously and thereby ensure an exact translational orbital movement of the first displacement disk 88. In order to prevent the first guide shaft 96 from rotating in the opposite direction to the direction of rotation of the drive shaft 72 and thus a pivoting of the first displacement disk 88 about its hub axis 108, a backstop (not shown) can be arranged or formed between the guide shaft 96 and the central housing 60.

The second compressor stage 110 is arranged in the second side housing 64. For this purpose, a second spiral-shaped stator blade 114 is formed on an inner end wall 112 of the second side housing 64. At least one second displacement blade 118 which is axially engaged with the second stator blade 114 is formed on a second displacement disk 116 which is rotatably mounted on an axially adjacent second eccentric pin 76 of the drive shaft 72 via a rolling bearing 120 designed as a cylindrical roller bearing. To guide the second displacement disk 116 when the drive shaft 72 is rotating in a translational orbital movement, a second guide device 122 is provided which has a second guide shaft 124 with a fourth eccentric pin 126 arranged on the outer circumference of the second displacement disk 116.

The eccentricity of the fourth eccentric pin 126 of the second guide shaft 124 is identical to that of the second eccentric pin 76 of the drive shaft 72. The main shaft of the second guide shaft 124 is rotatably mounted in a second bearing bore 130 of the central housing 60 via two roller bearings 128 designed as angular contact ball bearings. The fourth eccentric pin 126 on the second guide shaft 124 is rotatably mounted in a bearing bore 134 of the displacement disk 116 via two roller bearings 132 designed as angular contact ball bearings. When the displacement disk 116 is rotating, i.e. driven by the electric motor 66, When the drive shaft 72 is driven, the second guide shaft 124 should rotate synchronously and thereby ensure an exact translational orbital movement of the second displacement disk 116. In order to prevent the second guide shaft 124 from rotating in the opposite direction to the direction of rotation of the drive shaft 72 and thus the second displacement disk 116 from pivoting about its hub axis 136, a backstop (not shown) can be arranged or formed between the second guide shaft 124 and the central housing 60.

When the drive shaft 72 rotates, air or another gas is sucked through a first inlet connection 138 into a first inlet chamber 140 arranged in a ring around the blades 86, 90 of the first compressor stage 82 and is conveyed under compression into an outlet chamber 142 arranged centrally within the blades 86, 90 of the first compressor stage 82. From there, the correspondingly pre-compressed gas passes through an outlet connection 144, a pipe 146 and a second inlet connection 148 into a second inlet chamber 150 arranged in a ring around the blades 114, 118 of the second compressor stage 110. From there, the gas is conveyed under further compression into an outlet chamber 152 arranged centrally within the blades 114, 118 of the second compressor stage 110 and an outlet connection 154 leading from this to the outside.

The Indian 12 The two-stage scroll compressor 156 shown in a schematic longitudinal section differs from the one shown in the 11 illustrated spiral compressor 56 by two guide devices 166, 178 of the two compressor stages 82, 110 designed according to the invention and correspondingly simplified housing parts of the compressor housing 158, i.e. its central housing 160, first side housing 162 and second side housing 164. Various embodiments of these two guide devices 166, 178 are, as already described in detail, in the 1 to 1c and the 2 to 9 shown.

The guide device 166 of the first compressor stage 82 comprises a first guide lever 168 and a first support lever 174. The first guide lever 168 is aligned radially with respect to the hub axis 108 of the first displacement disk 88' and is rigidly attached to the first displacement disk 88' at its inner end 170. The first support lever 174 has spring-elastic properties and is made, for example, of rubber or another elastomeric plastic. The first support lever 174 is arranged with a tangential alignment to the hub axis 108 of the first displacement disk 88' between the radially outer end 172 of the first guide lever 168 and a projection 176 on the first side housing 162 of the compressor housing 158 and is firmly connected to each end. To simplify the illustration, the first guide lever 168 and the first support lever 174 are shown rotated from a diagonal arrangement with optical shortening of the first guide lever 168 into the drawing plane.

In the same construction, the guide device 178 of the second compressor stage 110 comprises a second guide lever 180 and a second support lever 186. The second guide lever 180 is aligned radially with respect to the hub axis 136 of the second displacement disk 116' and is rigidly attached to the second displacement disk 116' at its inner end 182. The second support lever 186 has spring-elastic properties and is made, for example, of rubber or another elastomeric plastic. The second support lever 186 is arranged with a tangential alignment to the hub axis 136 of the second displacement disk 116' between the outer end 184 of the second guide lever 180 and a projection 188 on the second side housing 164 of the compressor housing 158 and is firmly connected to each end. To simplify the illustration, the second guide lever 180 and the second support lever 186 are also shown here rotated from a diagonal arrangement with optical shortening of the second guide lever 180 into the plane of the drawing.

From the comparison of the known two-stage scroll compressor 56 with the inventive scroll compressor 156 according to the 11 and 12 It can be seen that the guide devices 166, 178 of the compressor stages 82, 110 ( 12 ) are significantly simpler and more space-saving and are easier to install. In addition, the proposed guide devices 166, 178 are friction-free and therefore wear-free.

List of reference symbols (part of the description)

2

Spiral compressors, scroll compressors

4

Compressor housing

6

Stator blade

8th

Displacement disc

10

Hub axle of the displacement disk

12

Displacement blade

14a, 14b

Outer crescent-shaped pressure chambers

16a, 16b

Inner sickle-shaped pressure chambers

18

drive shaft

20

Eccentric pin

22

Guide device

24

Guide lever

26

Inner end of the guide lever

28

Outer end of the guide lever

30

Support lever

30.1

Support lever (first embodiment)

30.2

Support lever (second embodiment)

30.3

Support lever (third embodiment)

30.4

Support lever (fourth embodiment)

30.5

Support lever (fifth embodiment)

30.6

Support lever (sixth embodiment)

30.7

Support lever (seventh embodiment)

30.8

Support lever (eighth embodiment)

30.9

Support lever (ninth embodiment)

36, 36'

Parallel outer sides of the support lever 30.3

38

Constriction on the support lever 30.5

40

First fitting on the support lever 30.6

42

Second fitting on support lever 30.6

44

Bolt connection on support lever 30.6

46

Rivet for bolt connection on support lever 30.6

48

Through hole on the support lever 30.7

50

Bearing bolt on guide lever 24

52

Bearing axis on support lever 30.8

54

Bearing bush on guide lever 24

56

Two-stage scroll compressor (state of the art)

58

Compressor housing of the scroll compressor 56

60

Central housing of the scroll compressor 56

62

First side casing of the compressor housing 58

64

Second side casing of the compressor housing 58

66

Electric motor

68

Stator of the electric motor

70

Rotor of the electric motor

72

drive shaft

74

First eccentric pin

76

Second eccentric pin

78

First rolling bearing, deep groove ball bearing

80

Second rolling bearing, deep groove ball bearing

82

First compressor stage of the scroll compressor

84

Inner front wall of the first side housing

86

First stator blade

88, 88'

First displacement disc

90

First displacement blade

92

Third rolling bearing, cylindrical roller bearing

94

First guidance system (state of the art)

96

First wave of leadership

98

Third eccentric pin

100

Rolling bearings, angular contact ball bearings

102

First bearing bore in the central housing 60

104

Rolling bearings, angular contact ball bearings

106

Bearing bore in the first displacement disc 88

108

First hub axle

110

Second compressor stage of the scroll compressor

112

Inner bulkhead of the second side housing

114

Second stator blade

116, 116'

Second displacement disc

118

Second displacement blade

120

Rolling bearings, cylindrical roller bearings

122

Second guidance device (state of the art)

124

Second wave of leadership

126

Fourth eccentric pin

128

Rolling bearings, angular contact ball bearings

130

Second bearing bore in the central housing 60

132

Rolling bearings, angular contact ball bearings

134

Bearing bore in the second displacement disk 116

136

Second hub axle

138

First input connection

140

First entrance room

142

First exit room

144

First output connection

146

Pipeline

148

Second input port

150

Second entrance room

152

Second exit room

154

Second output port

156

Two-stage scroll compressor (according to the invention)

158

Compressor housing (according to the invention)

160

Central housing of the compressor housing 158

162

First side casing of the compressor housing 158

164

Second side casing of the compressor housing 158

166

Guide device of the first compressor stage 82 (according to the invention)

168

Guide lever of the guide device 166

170

Inner end of guide lever 168

172

Outer end of guide lever 168

174

First support lever

176

Projection on the first side housing 162

178

Guide device of the second compressor stage 110 (according to the invention)

180

Guide lever of the guide device 178

182

Inner end of guide lever 180

184

Outer end of guide lever 180

186

Second support lever

188

Projection on the second side housing 164

d

Smaller diameter of the support lever 30.2

t

Reduced thickness of the support lever 30.4

QUOTES INCLUDED IN THE DESCRIPTION

This list of documents listed 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 accepts no liability for any errors or omissions.

Cited patent literature

• DE 3313000 A1 [0003]
• DE 3407939 C1 [0004]
• DE 102013218430 A1 [0005]

Claims (15)

Spiral compressor (2, 156), with at least one spiral-shaped stator blade (6, 86, 114) attached or formed on an inner end wall (84, 112) of a compressor housing (4, 158) and at least one spiral-shaped displacer blade (12, 90, 118) attached or formed on a displacement disk (8, 88', 116'), wherein the stator blade (6, 86, 114) and the displacement blade (12, 90, 118) axially engage with one another and delimit sickle-shaped pressure chambers (14a, 14b, 16a, 16b) between them, wherein the displacement disk (8, 88', 116') is rotatably mounted on an eccentric pin (20, 74, 76) of a drive shaft (18, 72) and at rotating drive shaft (18, 72) is guided in a translatory orbital movement by means of a guide device (22, 166, 178), characterized in that the guide device (22, 166, 178) has a guide lever (24, 168, 180) and a support lever (30, 174, 186), that the guide lever (24, 168, 180) is radially aligned with respect to the hub axis (10, 108, 136) of the displacement disk (8, 88', 116') and is rigidly attached to the displacement disk (8, 88', 116') with its inner end (26, 170, 182), that the support lever (30, 174, 186) has spring-elastic properties, and that the support lever (30, 174, 186) is the hub axle (10, 108, 136) of the displacement disc (8, 88', 116') is arranged with tangential alignment between the outer end (28, 172, 184) of the guide lever (24, 168, 180) and the compressor housing (4, 158) and is firmly connected to both. Scroll compressor according to Claim 1 , characterized in that the support lever (30, 30.1, 30.2, 30.3, 30.4, 30.5, 30.6, 30.7, 30.8) consists of rubber or another spring-elastic material, or that the support lever has at least one section which consists of a spring-elastic material. Scroll compressor according to Claim 2 , characterized in that the support lever (30.1) or the elastic portion of the support lever has a circular cross-section. Scroll compressor according to Claim 2 , characterized in that the support lever (30.2) or the elastic portion of the support lever has an elliptical cross-section and is arranged such that the smaller diameter (d) of the elliptical cross-section is aligned in the longitudinal direction of the guide lever (24). Scroll compressor according to Claim 2 , characterized in that the support lever (30.3) or the elastic portion of the support lever has a square cross-section and is arranged such that two opposite parallel outer sides (36, 36') of the square cross-sectional area are aligned in the longitudinal direction of the guide lever (24). Scroll compressor according to Claim 2 , characterized in that the support lever (30.4) or the elastic portion of the support lever has a cuboid-shaped cross-section and is arranged such that the smaller thickness (t) of the cuboid-shaped cross-sectional area is aligned in the longitudinal direction of the guide lever (24). Scroll compressor according to one of the Claims 2 until 6 , characterized in that the support lever (30.5) or the elastic portion of the support lever has a constriction (38) aligned in the longitudinal direction of the guide lever (24). Scroll compressor according to one of the Claims 2 until 7 , characterized in that the support lever (30, 30.1, 30.2, 30.3, 30.4, 30.5) is rigidly attached to the guide lever (24) and/or the compressor housing (4). Scroll compressor according to Claim 8 , characterized in that the support lever (30, 30.1, 30.2, 30.3, 30.4, 30.5) is molded onto a fitting of the guide lever (24) and/or a fitting of the compressor housing (4) by means of vulcanization or injection molding. Scroll compressor according to Claim 1 , characterized in that the support lever (30.9) consists of a spring plate and is curved radially outwards or inwards in a curved manner with respect to the hub axis (10) of the displacement disk (8). Scroll compressor according to one of the Claims 2 until 10 , characterized in that the support lever (30.6, 30.9) is fastened by means of a bolt connection (44) to a fitting of the guide lever (24) and/or to a fitting of the compressor housing (4). Scroll compressor according to one of the Claims 2 until 11 , characterized in that the support lever (30.7, 30.8) is articulated to the guide lever (24) and/or the compressor housing (4). Scroll compressor according to Claim 12 , characterized in that the support lever (30.7) with a centrally cylindrical through opening (48) widened in a V-shape on both sides is pivotably mounted on a central cylindrical bearing pin (50) of the guide lever (24), wherein the bearing pin (50) is aligned axially parallel to the hub axis (10) of the displacement disk (8). Scroll compressor according to Claim 12 , characterized in that the support lever (30.8) is pivotally mounted with an end-side bearing axis (52) in a bearing bush (54) which is rigidly fastened to the guide lever (24) and/or the compressor housing (4) and aligned axially parallel to the hub axis (10) of the displacement disk (8). Two-stage spiral compressor (156), having a first compressor stage (82) and a second compressor stage (110), each of which has a spiral-shaped stator blade (86, 114) attached or formed on an inner end wall (84, 112) of a compressor housing (158) and a spiral-shaped displacer blade (90, 118) attached or formed on a displacement disk (88', 116'), wherein the stator blade (86, 114) and the displacement blade (90, 118) axially engage with one another and delimit sickle-shaped pressure chambers (14a, 14b, 16a, 16b) between them, wherein the two displacement disks (88', 116') are rotatable at opposite ends of the compressor housing (158) on an eccentric pin (74, 76) of a common drive shaft (72) are mounted and are guided in a translatory orbital movement by means of a respective guide device (166, 178) when the drive shaft (72) rotates, characterized in that at least one of the guide devices (166, 178) has a guide lever (168, 180) and a support lever (174, 186) according to one of the preceding claims.

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