Scroll compressor
Patent Information
- Application Number
- EP2023798791
- Authority / Receiving Office
- EP · EP
- Patent Type
- Applications
- Current Assignee / Owner
- Priority Date
- 2022-12-07
- Filing Date
- 2023-11-01
- Publication Date
- 2025-10-15
AI Technical Summary
Existing scroll compressor guide devices are complex, require significant space, and suffer from wear due to high drive torque and frictional contact, leading to reduced efficiency and increased maintenance needs.
A scroll compressor with a guide device comprising a radially aligned guide lever and an elastic support lever, where the guide lever is attached to the displacement disk and the support lever is connected to the compressor housing, allowing for translational orbital movement with minimal pivoting and reduced wear through elastic absorption of deflection.
The solution provides a simple, space-efficient, and wear-free guide device that maintains high efficiency by minimizing pivoting of the displacement disk, reducing wear, and requiring fewer components, thus improving the overall performance and reliability of the scroll compressor.
Smart Images
Figure 1.1
Abstract
Description
[0001] Scroll compressor
[0002] Description
[0003] The invention relates to a scroll 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 engage with one another and delimit sickle-shaped pressure chambers between one another, wherein the displacer disk is rotatably mounted on an eccentric pin of a drive shaft and is guided in a translational orbital movement by means of a guide device when the drive shaft rotates.
[0004] Spiral compressors, also known as scroll compressors, are primarily used in stationary and mobile refrigeration units, heat pumps, and internal 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 displacer blade, which define several crescent-shaped pressure chambers between them. The stator blade is attached to an inner end wall of a compressor housing. The displacer blade, on the other hand, is arranged on a displacer 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 displacer disk with the displacer blade should perform a translational orbital movement to achieve high 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, meaning it should not pivot around its own hub axis if possible. If this is ensured, the blades can be designed and arranged such that the displacement blade approaches the stator blade in places to within a few micrometers. This ensures relatively good sealing of the pressure chambers, which are displaced circumferentially in the direction of rotation of the drive shaft and radially from outside to inside as the drive shaft rotates, reducing their volume i. However, to ensure the translational orbital movement of the displacement disk, a guide device is required, which can be designed in various ways.
[0005] In a scroll compressor known from DE 33 13 000 A1, 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 displacer disk via two rolling bearings. At the end facing the displacer 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 displacer disk by means of a rolling bearing. The guide shaft is drive-connected to the drive shaft via the toothed belt drive. With the same circumferential orientation of the eccentric pin of the drive shaft and the guide shaft, the guide gear ensures precise guidance of the displacer disk in a translational orbital movement when the drive shaft rotates.However, the disadvantages of such a guide gear are the high design effort, the large installation space requirement and the required high drive torque of the guide shaft.
[0006] DE 34 07 939 C1 describes a scroll compressor in which the guide device is formed by a rocker crank arranged tangentially on the outer circumference of the displacement disk as an extension of a displacement blade. The rocker crank is pivotally mounted 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 rocker crank is alternately deflected radially outward or inward about its outer bearing, causing a periodic pivoting of the displacement disk in the circumferential direction. The compact design of this known guide device is offset by the disadvantages of the rocker crank bearing, which is subject to wear, and the reduced efficiency of the scroll compressor due to the pivoting of the displacement disk.
[0007] In the scroll compressor known from DE 10 2013 218 430 A1, the guide device comprises an outer annular body fixed to the housing and having a cylindrical inner wall, an inner annular body having a cylindrical outer wall arranged coaxially within this outer annular body and connected to the displacer disk, and a plurality of conical thrust levers with cylindrical heads and spherical feet. Distributed around the circumference of the inner wall of the outer annular body are a plurality of cylindrical recesses which are aligned axially parallel to the drive axis. Distributed around the circumference of the outer wall of the inner annular body are the same number of radial guide openings. The thrust levers are pivotally mounted with their heads in the recesses of the outer annular body, and guided with their feet radially displaceable and pivotable in the guide openings of the inner annular body.This known guide device requires a comparatively large installation space and requires a high level of assembly effort. Furthermore, the guide device is subject to wear due to the frictional contact of the numerous thrust levers with the inner walls of the recesses and guide openings, requiring intensive lubrication of the contact areas.
[0008] 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 of simple construction, which takes up little installation space and is as wear-free as possible.
[0009] This object is achieved by a scroll compressor having the features of claim 1. Advantageous further developments are defined in the dependent claims.
[0010] Accordingly, the invention relates to a scroll 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 engage with one another and delimit sickle-shaped pressure chambers between one another, wherein the displacer disk is rotatably mounted on an eccentric pin of a drive shaft and is guided in a translational orbital movement by means of a guide device when the drive shaft rotates.
[0011] To achieve the stated object, this scroll compressor is provided with the guide device comprising a guide lever and a support lever, the guide lever being radially aligned with respect to the hub axis of the displacer disc and rigidly attached to the displacer disc 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 disc between the outer end of the guide lever and the compressor housing and being rigidly connected to both.
[0012] With the guide lever attached radially to the displacer disk and the elastic support lever arranged between the guide lever and the compressor housing, this guide device has a relatively simple design, 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 compressing. Since this is not entirely possible, this results in a periodic pivoting movement of the displacer disk around the hub axis, albeit only a few degrees. The pivoting movement of the displacer 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 as its circumferential arrangement can be chosen as desired.
[0013] The support lever can be made of rubber or another resilient material. Alternatively, the support lever can have at least one section made of a resilient material and therefore exhibit resilient properties. Since the elasticity of rubber decreases significantly at temperatures below freezing, an elastomeric plastic, which does not exhibit this property, is preferable for the support lever.
[0014] The support lever or the elastic portion of the support lever may have a circular cross-section.
[0015] 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.
[0016] 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.
[0017] Alternatively, it is also possible for the support lever or the elastic section 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.
[0018] Regardless 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 buckling hinge and thus further reduces the flexural rigidity of the support lever or the elastic section in the radial direction.
[0019] The support lever can be rigidly attached to the guide lever and / or the compressor housing. This can be achieved, for example, by vulcanizing or injection-molding the support lever onto a fitting of the guide lever and / or the compressor housing.
[0020] 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 order to enable bending, stretching and compression with respect to the hub axis of the displacement disc.
[0021] All of the support lever types mentioned can also be attached to a fitting on the guide lever and / or the compressor housing via a bolt connection, i.e., a screw, rivet, or split pin connection. In a support lever design made of rubber or another elastomeric plastic, it is provided with at least one vulcanized or overmolded fitting at the end.
[0022] However, the support lever can also be attached to the guide lever and / or the compressor housing in an articulated manner.
[0023] 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 disc.
[0024] Alternatively, however, it is also possible for the support lever, which for this purpose can be provided at the end with at least one vulcanized or overmolded fitting, to be pivotably mounted with at least one end-side bearing axis in a bearing bush which is aligned axially parallel to the hub axis of the displacement disc and rigidly fastened to the guide lever and / or the compressor housing.
[0025] The construction according to the invention can also be realized in a two-stage scroll compressor which has a first compressor stage and a second compressor stage.
[0026] The two compressor stages each have a spiral-shaped stator blade attached or formed on an inner end wall of a compressor housing, and a spiral-shaped displacer blade attached or formed on a displacer disk. The respective stator blade and the displacer blade assigned to it engage axially and define crescent-shaped pressure chambers between them. The two displacer disks are rotatably mounted at opposite ends of the compressor housing on an eccentric pin of a common drive shaft and, when the drive shaft rotates, are guided in a translational orbital movement by means of a guide device. According to the invention, the at least one guide device has a guide lever and a support lever according to the described design.
[0027] The invention will be further explained below with reference to several exemplary embodiments illustrated in the accompanying drawings. In the drawing, Fig. 1 shows a scroll compressor with a guide device according to the invention in a first functional position in a simplified axial view,
[0028] Fig. 1 a the scroll compressor according to Fig. 1 in a second functional position in a simplified axial view,
[0029] Fig. 1 b shows the scroll compressor according to Figures 1 and 1 a in a third functional position in a simplified axial view,
[0030] Fig. 1 c shows the scroll compressor according to Figures 1 to 1 b in a fourth functional position in a simplified axial view,
[0031] Fig. 2 shows a first embodiment of a guide device of a scroll compressor in a partial axial view,
[0032] Fig. 2a the guide device in a cross-sectional view AA according to Fig. 2,
[0033] Fig. 3 shows a second embodiment of a guide device of a scroll compressor in a partial axial view,
[0034] Fig. 3a the guide device in a cross-sectional view BB according to Fig. 3,
[0035] Fig. 4 shows a third embodiment of a guide device of a scroll compressor in a partial axial view,
[0036] Fig. 4a the guide device in a cross-sectional view CC according to Fig. 4,
[0037] Fig. 5 shows a fourth embodiment of a guide device of a scroll compressor in a partial axial view,
[0038] Fig. 5a the guide device in a cross-sectional view DD according to Fig. 5,
[0039] Fig. 6 shows a fifth embodiment of a guide device of a scroll compressor in a partial axial view,
[0040] Fig. 7 shows a sixth embodiment of a guide device of a scroll compressor in a partial axial view,
[0041] Fig. 8 shows a seventh embodiment of a guide device of a scroll compressor in a partial axial view,
[0042] Fig. 9 shows an eighth embodiment of a guide device of a scroll compressor in a partial axial view,
[0043] Fig. 10 shows a ninth embodiment of a guide device of a scroll compressor in a partial axial view,
[0044] Fig. 11 shows a two-stage scroll compressor with known guide devices in a schematic longitudinal section, and
[0045] Fig. 12 shows the two-stage scroll compressor according to Fig. 1 1 with guide devices according to the invention in a longitudinal center section. The simplified axial view according to Fig. 1 shows a scroll compressor 2 which has a spiral stator blade 6 fastened to an inner end wall (not shown) of a compressor housing 4 and a spiral displacer blade 12 arranged on a displacer 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 displacer disk 8 is rotatably mounted on an eccentric pin 20 of a drive shaft 18 and, when the drive shaft 18 rotates, is guided in a translational orbital movement by means of a guide device 22.
[0046] The guide device 22 comprises a guide lever 24 and a support lever 30. The guide lever 24 is radially aligned with respect to the hub axis 10 of the displacement disk 8 and is rigidly attached to the displacement disk 8 by its radially inner end 26. The support lever 30 is arranged tangentially aligned with respect to the hub axis 10 of the displacement disk 8 between the radially outer end 28 of the guide lever 24 and the compressor housing 4 and is firmly connected to both. The support lever 30 also has spring-elastic properties.
[0047] In Fig. 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 fluidly connected to an inlet chamber of the scroll compressor 2 (not visible in Fig. 1), while the radially inner pressure chambers 16a, 16b are completely closed. Due to the deflection of the displacer disk 8 by means of the eccentric pin 20, the support lever 30 is slightly elastically compressed in the 270° position and bent towards the displacer disk 8. In addition, the displacer disk 8 performed 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.
[0048] In the illustration shown in Fig. 1a, the drive shaft 18 has been rotated 90° clockwise compared to Fig. 1. Here, the scroll 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 scroll compressor 2. The radially inner pressure chambers 16a, 16b remain closed, but have further compressed the enclosed gas by reducing their volumes. Due to the vertical deflection of the displacer disk 8 upwards or radially outwards by means of the eccentric pin 20, the support lever 30 is elastically stretched and one end is bent away from the displacer disk 8.In addition, the displacement disk 8 performed a pivoting movement of two to three degrees clockwise with respect to the fictitious neutral position.
[0049] In Fig. 1b, the drive shaft 18 has been rotated a further 90° clockwise compared to the situation shown in Fig. 1a, and the scroll 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 scroll 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 an outlet chamber of the scroll compressor 2 that is formed radially inward and not visible in Fig. 1b. Due to the described deflection of the displacement disc 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 disc 8 performed a slight pivoting movement of less than one degree relative to the fictitious neutral position.
[0050] According to the illustration in Fig. 1 c, the drive shaft 18 has been rotated a further 90° clockwise compared to Fig. 1 b, and the scroll compressor 2 is thus 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 have been significantly reduced in size and have further compressed the gas enclosed therein. The radially inner pressure chambers 16a, 16b are now fully connected to the outlet chamber of the scroll compressor 2 (not visible here) and have almost completely expelled the previously enclosed gas into the outlet chamber. Due to the vertical downward deflection of the displacer disk 8 by means of the eccentric pin 20, the support lever 30 was elastically compressed and bent downward. In addition, the displacement disc 8 performed a larger pivoting movement of two to three degrees relative to the fictitious neutral position.Several possible embodiments of the support lever 30 are explained below with reference to Figures 2 to 10.
[0051] In the partial axial view of Fig. 2 and the cross-sectional view of Fig. 2a according to the sectional plane AA of Fig. 2, the support lever 30.1 in a first embodiment consists of rubber or another elastomeric plastic and has a circular cross-section.
[0052] In the partial axial view of Fig. 3 and the cross-sectional view of Fig. 3a along section plane BB of Fig. 3, the support lever 30.2, in a second embodiment, is also made of rubber or another elastomeric plastic, but has an elliptical cross-section. In order to achieve a lower spring stiffness in the radial direction relative 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.
[0053] In the partial axial view of Fig. 4 and the cross-sectional view of Fig. 4a along the sectional plane CC of Fig. 4, the support lever 30.3 in a third embodiment is also made of rubber or another elastomeric plastic, but now has a square cross-section. To achieve lower spring stiffness in the radial direction relative 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.
[0054] In the partial axial view of Fig. 5 and the cross-sectional view of Fig. 5a along section plane DD of Fig. 5, the support lever 30.4 in a fourth embodiment is also made of rubber or another elastomeric plastic, but has a cuboid cross-section. To achieve a lower spring stiffness in the radial direction relative 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 cross-sectional area is aligned in the longitudinal direction of the guide lever 24.
[0055] In the partial axial view of Fig. 6, the support lever 30.5, made of rubber or another elastomeric plastic, has, in a fifth embodiment, 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.
[0056] 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 formed onto a fitting of the guide lever 24 and / or the compressor housing 4 by means of vulcanization or injection molding.
[0057] In an alternative fastening method, the support lever 30.6 according to the sixth embodiment shown in Fig. 7 is fastened to a fitting 42 of the guide lever 24 by means of a vulcanized or overmolded first fitting 40 via a bolt connection 44. This bolt connection 44 is formed, for example, by a rivet 46 inserted into bores in the two fittings 40, 42.
[0058] In the partial axial view of Fig. 8, the support lever 30.7 made of rubber or another elastomeric plastic is, in a seventh embodiment, mounted in a form-fitting manner on a central cylindrical bearing pin 50 of the guide lever 24 by means of a through opening 48 which is cylindrical in the middle and widened in a V-shape on the outside, wherein the bearing pin 50 is aligned axially parallel to the hub axis 10 of the displacement disk 8.
[0059] According to an alternative eighth embodiment, a support lever 30.8, depicted in a partial axial view of Fig. 9 and made of rubber or another elastomeric plastic, is pivotally mounted by means of a bearing spindle 52 attached to the support lever 30.8 at the end in a bearing bush 54 rigidly attached to the guide lever 24 and aligned axially parallel to the hub axis 10 of the displacement disk 8. For this purpose, the bearing spindle 52 of the support lever 30.8 can be a component of a fitting vulcanized or overmolded into the end of the support lever 30.8.
[0060] In the partial axial view of Fig. 10, the support lever 30.9 according to a ninth embodiment consists of a spring plate which is curved radially outward in an arc shape relative to the hub axis 10 of the displacement disk 8 to enable its bending, stretching, and compression. In the present case, the support lever 30.9 is fastened to a fitting 42 of the guide lever 24 via a bolt connection 44, analogous to the sixth embodiment of the support lever 30.6 according to Fig. 7, wherein the bolt connection 44 is formed by a rivet 46 inserted into bores in the support lever 30.9 and the fitting 42.
[0061] Fig. 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.
[0062] 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 either side thereof. 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.
[0063] 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 displacer blade 90, which is axially engaged with this first stator blade 86, is formed on a first displacer disk 88. This first displacer disk 88 is rotatably mounted on an axially adjacent first eccentric pin 74 of the drive shaft 72 via a third rolling bearing 92 designed as a cylindrical roller bearing. To guide the first displacer disk 88 when the drive shaft 72 rotates in a translational orbital movement, a known guide device 94 is provided which comprises a first guide shaft 96, which is arranged on the outer circumference of the first displacer disk 88 and has a third eccentric pin 98.
[0064] 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.
[0065] When the drive shaft 72 rotates, i.e., driven by the electric motor 66, the first guide shaft 96 should rotate synchronously, thereby ensuring a precise translational orbital movement of the first displacement disk 88. To prevent rotation of the first guide shaft 96 counter to the direction of rotation of the drive shaft 72 and thus 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.
[0066] The second compressor stage 110 is arranged in the second side housing 64. For this purpose, a second spiral stator blade 114 is formed on an inner end wall 112 of the second side housing 64. At least one second displacer blade 118, which is axially engaged with the second stator blade 114, is formed on a second displacer 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 displacer disk 116 in a translational orbital movement when the drive shaft 72 rotates, a second guide device 122 is provided, which has a second guide shaft 124 arranged on the outer circumference of the second displacer disk 116 and having a fourth eccentric pin 126.
[0067] 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 angular-contact ball bearings 128. 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 angular-contact ball bearings 132. When the drive shaft 72 rotates, i.e., when driven by the electric motor 66, the second guide shaft 124 should rotate synchronously, thereby ensuring a precise translational orbital movement of the second displacement disk 116.In order to prevent rotation of the second guide shaft 124 counter to the direction of rotation of the drive shaft 72 and thus pivoting of the second displacement disk 116 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.
[0068] 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 via 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.
[0069] The two-stage scroll compressor 156 shown in Fig. 12 in a schematic longitudinal center section differs from the scroll compressor 56 shown in Fig. 11 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 shown, as already described in detail, in Figs. 1 to 1c and Figs. 2 to 9.
[0070] 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 radially aligned 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, for this purpose, is made, for example, of rubber or another elastomeric plastic. The first support lever 174 is arranged, tangentially aligned 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 thereof.To simplify the illustration, the first guide lever 168 and the first support lever 174 are shown rotated from a diagonal arrangement with optical foreshortening of the first guide lever 168 into the plane of the drawing.
[0071] 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, for this purpose, is made, for example, of rubber or another elastomeric plastic. The second support lever 186 is arranged, tangentially aligned 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 thereof.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 the second guide lever 180 optically shortened into the plane of the drawing.
[0072] Comparing the known two-stage scroll compressor 56 with the scroll compressor 156 designed according to the invention, as shown in Figures 11 and 12, it is evident that the guide devices 166, 178 of the compressor stages 82, 110 (Figure 12) designed according to the invention are significantly simpler and more space-saving, as well as easier to install. Furthermore, the proposed guide devices 166, 178 operate friction-free and thus wear-free.
[0073] List of reference symbols (part of the description)
[0074] Scroll compressors
[0075] Compressor housing
[0076] Stator blade
[0077] Displacement disc
[0078] Hub axis of the displacer disc
[0079] Displacement blade a, 14b Outer crescent-shaped pressure chambers a, 16b Inner crescent-shaped pressure chambers
[0080] drive shaft
[0081] Eccentric pin
[0082] Guide device
[0083] Guide lever
[0084] Inner end of the guide lever
[0085] Outer end of the guide lever
[0086] Support lever .1 Support lever (first embodiment) .2 Support lever (second embodiment) .3 Support lever (third embodiment) .4 Support lever (fourth embodiment) .5 Support lever (fifth embodiment) .6 Support lever (sixth embodiment) .7 Support lever (seventh embodiment) .8 Support lever (eighth embodiment) .9 Support lever (ninth embodiment) , 36' Parallel outer sides of the support lever 30.3
[0087] Constriction on the support lever 30.5
[0088] First fitting on the support lever 30.6
[0089] Second fitting on the support lever 30.6
[0090] Bolt connection on the support lever 30.6
[0091] Rivet for bolt connection on support lever 30.6
[0092] Through hole on the support lever 30.7
[0093] Bearing pin on the guide lever 24 Bearing axis on the support lever 30.8 Bearing bush on the guide lever 24
[0094] Two-stage scroll compressor (state of the art)
[0095] Compressor housing of the scroll compressor 56
[0096] Central housing of the scroll compressor 56
[0097] First side casing of the compressor housing 58
[0098] Second side casing of the compressor housing 58
[0099] electric motor
[0100] Stator of the electric motor
[0101] Rotor of the electric motor
[0102] drive shaft
[0103] First eccentric pin
[0104] Second eccentric pin
[0105] First rolling bearing, deep groove ball bearing
[0106] Second rolling bearing, deep groove ball bearing
[0107] First compressor stage of the scroll compressor
[0108] Inner front wall of the first side housing
[0109] First stator blade, 88' First displacer disc
[0110] First displacement blade
[0111] Third rolling bearing, cylindrical roller bearing
[0112] First guidance device (state of the art)
[0113] First wave of leadership
[0114] Third eccentric pin 0 Rolling bearing, angular contact ball bearing 2 First bearing bore in the central housing 60 4 Rolling bearing, angular contact ball bearing 6 Bearing bore in the first displacement disk 888 First hub axle 0 Second compressor stage of the scroll compressor 2 Inner end wall of the second side housing 4 Second stator blade 6, 116' Second displacement disk 8 Second displacement blade 0 Rolling bearing, cylindrical roller bearing 2 Second guide device (state of the art) 124 Second guide shaft
[0115] 126 Fourth eccentric pin
[0116] 128 rolling bearings, angular contact ball bearings
[0117] 130 Second bearing bore in the central housing 60
[0118] 132 rolling bearings, angular contact ball bearings
[0119] 134 Bearing bore in the second displacement disc 116
[0120] 136 Second hub axle
[0121] 138 First input connection
[0122] 140 First entrance room
[0123] 142 First Exit Room
[0124] 144 First output connection
[0125] 146 pipeline
[0126] 148 Second input connection
[0127] 150 Second entrance room
[0128] 152 Second Exit Room
[0129] 154 Second output connection
[0130] 156 Two-stage scroll compressor (according to the invention)
[0131] 158 Compressor housing (according to the invention)
[0132] 160 Central housing of the compressor housing 158
[0133] 162 First side casing of the compressor housing 158
[0134] 164 Second side casing of the compressor housing 158
[0135] 166 Guide device of the first compressor stage 82 (according to the invention)
[0136] 168 Guide lever of the guide device 166
[0137] 170 Inner end of the guide lever 168
[0138] 172 Outer end of the guide lever 168
[0139] 174 First support lever
[0140] 176 Projection on the first side housing 162
[0141] 178 Guide device of the second compressor stage 110 (according to the invention)
[0142] 180 Guide lever of the guide device 178
[0143] 182 Inner end of the guide lever 180
[0144] 184 Outer end of the guide lever 180
[0145] 186 Second support lever
[0146] 188 Projection on the second side housing 164 d Smaller diameter of the support lever 30.2 t Smaller thickness of the support lever 30.4
Claims
Patent claims 1 . A scroll compressor (2, 156) comprising at least one spiral stator blade (6, 86, 114) secured or formed on an inner end wall (84, 112) of a compressor housing (4, 158) and at least one spiral displacer blade (12, 90, 118) secured or formed on a displacer disk (8, 88', 116'), wherein the stator blade (6, 86, 114) and the displacer blade (12, 90, 118) axially engage with one another and define sickle-shaped pressure chambers (14a, 14b, 16a, 16b) between them, wherein the displacer disk (8, 88', 116') is rotatably mounted on an eccentric pin (20, 74, 76) of a drive shaft (18, 72) is mounted and is guided in a translatory orbital movement by means of a guide device (22, 166, 178) when the drive shaft (18, 72) is rotating, 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 disc (8, 88', 116') and is rigidly attached to the displacement disc (8, 88', 116') by 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 arranged with a tangential alignment with respect to the hub axis (10, 108, 136) of the displacement disc (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.
2. 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.
3. 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.
4. 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).
5. Scroll compressor according to claim 2, characterized in that the support lever (30.3) or the elastic section 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).
6. Scroll compressor according to claim 2, characterized in that the support lever (30.4) or the elastic section of the support lever has a cuboid cross-section and is arranged such that the smaller thickness (t) of the cuboid cross-sectional area is aligned in the longitudinal direction of the guide lever (24).
7. Scroll compressor according to one of claims 2 to 6, characterized in that the support lever (30.5) or the elastic section of the support lever has a constriction (38) aligned in the longitudinal direction of the guide lever (24).
8. Scroll compressor according to one of claims 2 to 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).
9. Scroll compressor according to claim 8, characterized in that the support lever (30, 30.1, 30.2, 30.3, 30.4, 30.5) is formed by means of vulcanization or injection molding onto a fitting of the guide lever (24) and / or a fitting of the compressor housing (4).
10. 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 an arc shape with respect to the hub axis (10) of the displacement disc (8). 1 1. Scroll compressor according to one of claims 2 to 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).
12. Scroll compressor according to one of claims 2 to 11, characterized in that the support lever (30.7, 30.8) is articulated to the guide lever (24) and / or the compressor housing (4).
13. Scroll compressor according to claim 12, characterized in that the support lever (30.7) with a centrally cylindrical through opening (48) which is widened in a V-shape on both sides and is pivotably mounted on a central cylindrical bearing pin (50) of the guide lever (24), the bearing pin (50) being aligned axially parallel to the hub axis (10) of the displacement disc (8).
14. 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) rigidly fastened to the guide lever (24) and / or the compressor housing (4) and aligned axially parallel to the hub axis (10) of the displacer disk (8).
15. Two-stage scroll compressor (156), comprising a first compressor stage (82) and a second compressor stage (110), each having a spiral stator blade (86, 114) attached or formed on an inner end wall (84, 112) of a compressor housing (158) and a spiral displacer blade (90, 118) attached or formed on a displacer disk (88', 116'), wherein the stator blade (86, 114) and the displacer blade (90, 118) axially engage with one another and define sickle-shaped pressure chambers (14a, 14b, 16a, 16b) between them, wherein the two displacer disks (88', 116') are rotatably mounted on an eccentric pin at opposite ends of the compressor housing (158). (74, 76) of a common drive shaft (72) and are guided in a translatory orbital movement by means of a respective guide device (166, 178) when the drive shaft (72) is rotating, characterized in thatthat 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.,
Citation Information
Patent Citations
Scroll pump
GB2614581B