Scroll compressor for producing oil-free compressed air

Abstract

A scroll compressor for producing oil-free compressed air, in particular for a compressed air brake system of a heavy goods vehicle, has a drive which is arranged in a housing (4) and is connected to a rotary volumetric spiral (31, 32) which has a volumetric spiral bottom (39) and a volumetric spiral wall (38), wherein the volumetric spiral wall (38) engages into a stationary counter spiral (21, 22) such that at least one variable compression chamber (30) is formed between the volumetric spiral (31, 32) and the counter spiral (21, 22), wherein a sealing element (33) is provided between the volumetric spiral (31, 32) and the housing (4), and wherein the sealing element (33) is fastened in the volumetric spiral bottom (39) and seals against a sliding plate (26) which is firmly connected to the housing (4). A compressed air brake system having such a scroll compressor.

Description

[0001] This invention relates to a scroll compressor for producing oil-free compressed air. Furthermore, this invention relates to a compressed air braking system having such a scroll compressor.

[0002] Scroll compressors are known from the prior art and are used in a variety of applications. EP 0 798 463 A2 discloses a vacuum pump designed as a scroll compressor. The vacuum pump is used to evacuate containers and operates without oil. For this purpose, the vacuum pump has a scroll compressor having a rotating positive displacement screw connected to a driver, the positive displacement screw engaging with a fixed mating screw. The fixed mating screws are firmly integrated into a housing. The positive displacement screw includes a bottom and a wall, wherein the wall of the positive displacement screw engages in a corresponding space in the wall of the mating screw, such that a variable compression chamber is formed between the wall of the positive displacement screw and the wall of the mating screw.

[0003] To ensure airtightness, an annular seal is provided in the housing to seal the bottom of the volumetric auger. Furthermore, the walls of the volumetric auger and the mating auger each have helical grooves into which the helical seal is inserted, sealing the housing at the bottom of the volumetric auger or in the area at the bottom end of the mating auger wall.

[0004] The positive displacement screw rotates around the annular seal during the operation of the scroll compressor. This can cause oil present in the drive section of the scroll compressor to be transported by the positive displacement screw above the annular seal, potentially allowing oil to enter the compression chamber. Furthermore, friction between the bottom of the positive displacement screw and the annular seal can accelerate wear on the annular seal, thus potentially creating a channel for oil overflow.

[0005] Therefore, in known scroll compressors, there is a risk that the compression chamber cannot be kept completely oil-free. When used as a vacuum pump, this is not serious because the compressed gas and any incoming oil in the compression chamber are discharged into the surrounding environment. However, in closed loops, such as in compressed air braking systems, this oil ingress is serious because oil can accumulate in the closed gas circuit.

[0006] The objective of this invention is to provide a scroll compressor for generating oil-free compressed air, wherein oil is effectively prevented from entering the compression zone. Furthermore, the objective of this invention is to provide a compressed air braking system incorporating such a scroll compressor.

[0007] According to the present invention, the tasks related to the scroll compressor are achieved by the scroll compressor described below, and the tasks related to the compressed air braking system are achieved by the compressed air braking system described below.

[0008] Therefore, the present invention is based on the following concept: providing a scroll compressor for generating oil-free compressed air, particularly a scroll compressor for a compressed air braking system of heavy-duty vehicles, the scroll compressor having a driver arranged in a housing and connected to a rotating positive displacement screw. The positive displacement screw has a bottom and a wall, wherein the wall engages with a fixed mating screw, such that at least one variable compression chamber is formed between the positive displacement screw and the mating screw. According to the invention, a sealing element is provided between the positive displacement screw and the housing, wherein the sealing element is fastened in the bottom of the positive displacement screw and seals a sliding plate firmly connected to the housing.

[0009] To ensure an efficient and durable oil barrier between the drive zone and the compression zone of the scroll compressor, this invention proposes that a sealing element is secured to the bottom of a volumetric screw and seals a sliding plate secured in the housing. Here, the sliding plate can be designed to achieve a good seal between the sliding plate and the sealing element while minimizing friction. This effectively counteracts excessive wear on the sealing element, thereby maintaining high sealing performance over a long period.

[0010] Furthermore, arranging the sealing element at the bottom of the positive displacement screw assembly improves the maintainability of the scroll compressor according to the invention. In the event of a defect in the sealing area, the seal can be replaced quickly by replacing the entire positive displacement screw assembly (including the seal disposed therein). In the prior art, an additional handle is required to replace the sealing element in the housing after removing the positive displacement screw assembly. In this invention, this can be achieved simply and quickly by replacing the positive displacement screw assembly with an integrated sealing element. Therefore, the scroll compressor can be quickly put back into service.

[0011] In a preferred embodiment of the invention, the sliding plate has a harder material than the housing, at least in the contact area with the sealing element. Furthermore, the sliding plate may have a lower surface roughness than the housing on the side facing the sealing element. Therefore, essentially, the sliding plate serves to provide good contact with the sealing element on one hand, and to reduce friction between the sliding plate and the sealing element on the other. Since the sealing element moves with the volumetric screw, i.e., moves on the sliding plate, the harder material of the sliding plate in this area prevents or reduces wear on the sealing element. In this respect, the sliding plate, particularly the sliding plate with a harder material in the contact area with the sealing element, forms the basis for a good, and especially oil-proof, seal between the drive and compression regions of the scroll compressor. Therefore, it is ensured that oil does not enter the compression region from the drive region. This ensures the oil-free nature of the generated compressed air.

[0012] As an additional safety barrier, a wiping element for removing oil residue from the sliding plate can also be secured in the bottom of the volumetric auger. The wiping element is preferably arranged parallel or concentrically to the sealing element and serves to remove any oil residue that may deposit on the contact area between the sliding plate and the sealing element. This ensures that the regularly arranged area of ​​the sliding plate in the compression zone does not introduce oil into the compression zone. Such an area arises because the circumferential movement of the volumetric auger establishes a contact area on the sliding plate, which is sometimes located in the compression zone and sometimes in the drive zone. Wiping away any oil that may deposit on this contact area of ​​the sliding plate by the wiping element ensures that the section of the sliding plate entering the compression zone is oil-free.

[0013] To securely house the sealing element and / or wiping element within the volumetric screw, a preferred variant of the invention proposes that the bottom of the volumetric screw has a sealing groove for accommodating the sealing element and / or a wiping groove for accommodating the wiping element. Additional pre-tightening elements may be arranged within the sealing groove and / or wiping groove, extending between the bottom of the groove and the sealing element or wiping element. These pre-tightening elements generate pressing pressure on the sealing element or wiping element against the sliding plate, thereby persistently ensuring the sealing or wiping function, especially when the sealing element and / or wiping element experience slight wear.

[0014] A sliding element can also be arranged between the positive displacement screw and the sliding plate. The sliding element can be designed as an axial bearing, and the positive displacement screw is supported on the sliding plate or housing. Preferably, the sliding element is made of a material that slides particularly well on the sliding plate. In particular, the sliding element works together with the sliding plate to reduce the friction between the positive displacement screw and the housing, thereby facilitating the rotation of the positive displacement screw. This reduces the energy required to operate the scroll compressor and the frictional heat generated during operation.

[0015] The sliding element can be arranged in a recess in the bottom of the volumetric screw. On the one hand, this allows the sliding element to be better fixed in a predetermined position. On the other hand, the sliding element can be easily replaced along with the volumetric screw in this way, for example, for repair purposes.

[0016] To further improve the sliding characteristics of the sliding element, it is proposed to arrange the sliding element radially within the sealing element and / or wiping element. Therefore, essentially, the sliding element can be arranged in the oiled area of ​​the scroll compressor, particularly the drive area. This provides additional oil lubrication between the sliding element and the sliding plate, resulting in smooth rotation of the positive displacement screw.

[0017] In the scroll compressor according to the invention, guide pins are also proposed to be anchored in the housing, extending through openings in the sliding plate into guide rings arranged at the bottom of the positive displacement screw. Each guide pin has a shoulder (Absatz) protruding beyond the sliding plate, creating a gap between the respective guide ring and the sliding plate. The combination of guide pins and guide rings is referred to as a "pin-ring" system, which facilitates the circumferential motion of the positive displacement screw. By engaging the guide pins in the guide rings, the positive displacement screw is forced into a predetermined rotational path, formed by an eccentric support of the positive displacement screw on the shaft of the drive.

[0018] To further minimize friction, it is advantageously proposed that the guide pin have a shoulder that protrudes beyond the sliding plate. This creates a gap between the guide ring and the sliding plate, reducing friction in this area. Furthermore, the gap between the guide ring and the sliding plate enables oil lubrication of the sliding plate.

[0019] In a particularly preferred embodiment of the invention, the drive is arranged between the first and second positive displacement screw components. Therefore, the scroll compressor can be designed as a multi-stage, particularly a two-stage, scroll compressor. Thus, pre-compression can occur in the first compression stage, and post-compression in the second compression stage, thereby achieving particularly high pressures. This is particularly advantageous for generating compressed air for compressed air braking systems, especially in heavy-duty vehicles.

[0020] In this regard, a preferred variant further proposes that the drive has a shaft with two ends, wherein a first end is connected to a first positive displacement screw, and a second end is connected to a second positive displacement screw. Thus, the positive displacement screws share the same drive, which improves the efficiency of the scroll compressor and advantageously reduces its structural size. Therefore, this two-stage scroll compressor is particularly compact.

[0021] Here, a first volumetric screw can form a first compressor stage with a first mating screw, and a second volumetric screw can form a second compressor stage with a second mating screw. The compressor stages can be interconnected, such that, for example, the first compressor stage can perform pre-compression, and the second compressor stage can perform post-compression. This allows for particularly high pressures, which is especially advantageous for generating compressed air (particularly for compressed air braking systems in heavy-duty vehicles). The connection between the first and second compressor stages can be made via external piping. However, the piping for connecting the two compressor stages can also be integrated into the casing of the scroll compressor. In any case, it is preferable to arrange a heat exchanger between the first and second compressor stages, which dissipates heat from the pre-compressed compressed air, thereby supplying cooled, pre-compressed compressed air to the second compressor stage.

[0022] Specifically, it can be proposed that the first compressor stage causes compression from the intake pressure to the intermediate air pressure. Here, the intake pressure can be, for example, about 1 bar, while the intermediate air pressure is in the range of 3.5 bar to 4 bar. Then, the second compressor stage can cause even higher compression from the intermediate air pressure to the high air pressure. Here, it is preferable that the intermediate air pressure between 3.5 bar and 4 bar is compressed to a high air pressure in the range of about 14 bar.

[0023] Preferably, the first and second shaft ends are respectively equipped with radial bearings, particularly eccentric bearings. The radial or eccentric bearings can be designed as sliding bearings, ball bearings, or needle roller bearings. A balancing mechanism can be arranged between the first shaft end and the first volumetric screw and / or between the second shaft end and the second volumetric screw. This balancing mechanism reduces vibrations generated during the oscillating motion of the volumetric screw, thereby reducing noise. Such a balancing mechanism includes a balance block eccentrically arranged on the rotating shaft of the oscillating volumetric screw and capable of oscillating about this shaft. Here, the balancing mechanism is designed to autonomously adjust for vibrations caused by existing centrifugal forces. Here, the balancing mechanism achieves compensation for gas forces and manufacturing tolerances, thereby reducing vibrations and noise generated during the operation of the scroll compressor.

[0024] For example, a balancing mechanism that can be particularly preferably used in the scroll compressor according to the invention is described in subsequently published German patent application 10 2020 121 442.1, the contents of which are fully referenced, particularly in relation to the invention. Figure 2 The content related to the embodiments.

[0025] In another variation of the invention, spiral seals are provided between the wall of the positive displacement screw and the mating screw, and between the wall of the mating screw and the positive displacement screw. Therefore, the positive displacement screw and the mating screw are well-sealed, forming a closed, substantially leak-free variable compression space. Here, the spiral seals also compensate for manufacturing tolerances and pressure fluctuations in the compression chamber. In this respect, the scroll compressor can eliminate the back pressure chamber or counter-pressure chamber, which typically uses pressure from the compression chamber to press the rotating positive displacement screw against the mating screw. By eliminating the back pressure chamber, installation space is saved, thereby making the scroll compressor particularly compact.

[0026] Preferably, the first helical seal is arranged in a helical groove on the wall of the volumetric helical member that opens towards the mating helical member. The second helical seal can be arranged in a helical groove on the wall of the mating helical member that opens towards the volumetric helical member. Therefore, essentially, the helical grooves in both the wall of the volumetric helical member and the wall of the mating helical member accommodate and secure their respective helical seals. To reduce friction between the volumetric helical member and the mating helical member, a thrust plate can be assigned to each helical seal. Preferably, the thrust plate is arranged between the corresponding helical seal and the volumetric helical member or the mating helical member, thereby reducing friction between them. Here, the thrust plate is pushed against the corresponding volumetric helical member or the mating helical member by the helical seal, thus achieving both a sealing function and a sliding function.

[0027] In a preferred variant of the scroll compressor according to the invention, the drive and / or housing and / or mating screws are water-cooled. Water cooling is particularly effective and enables high and rapid heat dissipation, thus allowing the scroll compressor to operate at particularly high pressures. This is particularly advantageous for compressed air braking systems in heavy-duty vehicles. Special attention can be paid to cooling the housing, particularly the high-pressure side or exhaust side of the scroll compressor. In this region, especially in the region of the second compressor stage, the temperature can be effectively dissipated by water cooling, as high-pressure compression can generate particularly high temperatures. Furthermore, it is advantageous to cool the compressed air generated in the scroll compressor. Preferably, a heat exchanger is disposed between the first and second compressor stages, dissipating heat from the compressed air compressed to a medium air pressure. Thus, the pre-cooled medium compressed air enters the second compressor stage, where it is further compressed to high compressed air.

[0028] A parallel aspect of the invention relates to a compressed air braking system, particularly a compressed air braking system for heavy-duty vehicles, which has the aforementioned scroll compressor. However, such a compressed air braking system can be used not only for heavy-duty vehicles, but also, for example, for buses or construction machinery (e.g., excavators, road rollers, self-propelled cranes, etc.). In any case, such a compressed air braking system is particularly suitable for vehicles with a gross vehicle weight exceeding 5 tons.

[0029] The invention will now be described in more detail based on embodiments and with reference to the accompanying schematic diagrams. In the drawings:

[0030] Figure 1 A cross-sectional view of a scroll compressor according to a preferred embodiment of the invention is shown;

[0031] Figure 2 It shows that according to Figure 1 The local C of the scroll compressor;

[0032] Figure 3 It shows that according to Figure 1 A front view of a scroll compressor; and

[0033] Figure 4 It shows that according to Figure 1 The scroll compressor along Figure 3 A cross-sectional view of line EE.

[0034] according to Figure 1 The scroll compressor is designed as a two-stage compressor. For this purpose, the scroll compressor has a central drive section 1, which is axially connected to compressor sections 2 and 3 on either side. Here, the first compressor section 2 is designed as the first compressor stage, and the second compressor section 3 is designed as the second compressor stage. The first compressor section 2 is used to compress ambient air pressure to a medium air pressure, while the second compressor section 3 compresses the medium air pressure to a high air pressure.

[0035] Drive section 1 includes a driver 10, which includes an electric motor 11 and a shaft 12. The electric motor 11 is arranged within a housing 4, which is designed as a multi-piece unit for maintenance-friendly reasons. Therefore, housing 4 includes a driver housing 20, two bearing housings 23 and 24 connected to the driver housing 20, mating screws 21 and 22 also forming part of housing 4, and end caps 5 and 6. Thus, in the direction of the first compressor section 2, the first bearing housing 23 is connected to the driver housing 20. The first bearing housing 23 is securely connected to the first mating screw 21, which also forms part of housing 4. Following the first mating screw 21 is the first end cap 5, which axially closes housing 4. On the opposite side of the driver housing 20, a second bearing housing 24 is arranged, connected to the second mating screw 22. The second mating screw 22 is covered longitudinally by the second end cap 6.

[0036] Shaft 12 is supported in drive housing 20 by bearing 15. Shaft 12 has a first shaft end 13 pointing towards the first compressor section 2. Furthermore, a second shaft end 14 facing the second compressor section 3 is also provided. Each of these shaft ends 13, 14 has an eccentric pin 16, which is arranged in an eccentric bearing 17, establishing a connection with a corresponding volumetric screw 31, 32. Thus, the first volumetric screw 31 is supported on the eccentric pin 16 of the first shaft end 13 by the eccentric bearing 17. The second volumetric screw 32 is supported on the eccentric pin 16 of the second shaft end 14 by the eccentric bearing 17.

[0037] The volumetric screws 31 and 32 each have a volumetric screw bottom 39, and a volumetric screw wall 38 extends from the volumetric screw bottom 39 into their respective mating screws 21 and 22. This is based on the following... Figure 2 Exemplary illustration, Figure 2 It shows that according to Figure 1 The design described below for the first compressor stage 2 of the scroll compressor is similarly applicable to the second compressor stage 3. Therefore, the construction of the first positive displacement screw 31 and the second positive displacement screw 32, as well as the first mating screw 21 and the second mating screw 22, are similar, particularly in their arrangement relative to each other. Their only difference lies in the volume of the compression chamber 30 formed between them, which in the second compressor stage (i.e., between the second positive displacement screw 32 and the second mating screw 22) is smaller than the volume in the first compressor stage (i.e., between the first positive displacement screw 31 and the first mating screw 21).

[0038] therefore, Figure 2 A first volumetric auger 31 is shown, comprising a volumetric auger bottom 39 and a volumetric auger wall 38. The first volumetric auger 31 engages with a first mating auger 21, such that a compression chamber 30 is formed between the volumetric auger wall 38 and the mating auger wall 28. The compression chamber 30 is variable, meaning that the volume of the compression chamber 30 changes due to the circumferential movement of the first volumetric auger 31, thereby compressing the gas (preferably air) within the compression chamber 30.

[0039] To ensure a good seal between the first commissive auger 31 and the first mating auger 21, both the first commissive auger 31 and the first mating auger 21 are provided with helical grooves 19, in which helical seals 18 are arranged. Here, the helical seal 18 of the first commissive auger 31 seals the bottom 29 of the mating auger of the first mating auger 21. Conversely, the helical seal 18 of the first mating auger 21 seals the bottom 39 of the commissive auger. Each helical seal may include thrust plates arranged between the respective helical groove 19 and the bottom 39 of either the commissive auger or the mating auger.

[0040] To guide the first volumetric auger 31 in its circumferential motion, a plurality of guide rings 37 are arranged in the bottom 39 of the volumetric auger. The guide rings 37 accommodate guide pins 25, which are fixed in the first bearing housing 23. Each guide pin 25 includes an anchoring section 25a, which is held in a corresponding hole in the first bearing housing 23. A guide section 25b of the guide pin 25 engages in the guide ring 37. A shoulder 25c is formed between the guide section 25b and the anchoring section 25a. The shoulder 25c is formed specifically by the fact that the diameter of the guide section 25b is smaller than the diameter of the anchoring section 25a.

[0041] Preferably, the anchoring section 25a is not completely recessed into the corresponding hole of the first bearing housing 23. Instead, the shoulder 25c of the anchoring section 25a protrudes beyond the first bearing housing 23. The guide ring 37 is located on the shoulder 25c. Because the shoulder 25c protrudes beyond the first bearing housing 23, a gap is formed between the guide ring 37 and the sliding plate 26 fixed in the first bearing housing 23. Therefore, oil for lubricating the drive section 1 can flow between the guide ring 37 and the sliding plate 26, thereby lubricating the sliding plate 26.

[0042] Preferably, the sliding plate 26 is designed to be annular and includes a through hole through which the guide pin 25 can extend. On the side facing the first bearing housing 23, the sliding plate 26 can be sealed with an annular seal 27. Here, the annular seal 27 is arranged in a circumferential groove in the first bearing housing 23.

[0043] The first volumetric auger 31 is positioned on the sliding plate 26 via a sliding element 36. Specifically, the sliding element 36, in the form of a sliding ring, is radially arranged within the guide pin 25, and this sliding ring is positioned in a groove in the bottom 29 of the volumetric auger. The sliding element 36 may protrude slightly beyond the bottom 39 of the volumetric auger, such that essentially only the sliding element 36 slides on the sliding plate 26. Therefore, there is a certain distance between the bottom 39 of the volumetric auger and the sliding plate 26. Preferably, the sliding element 36 also serves as an axial bearing for the first volumetric auger 31. Here, the sliding element 36 is lubricated with a liquid, preferably with oil. Typically, the bearing 15 can also be lubricated with oil. However, the bearing 15 can also be lubricated with grease.

[0044] To prevent oil from entering the first compressor section 2 from the drive section 1, a sealing system is provided. The sealing system includes a sealing element 33 and a wiping element 34. The sealing element 33 and the wiping element 34 are each designed to be annular and are fastened in corresponding annular grooves in the first volumetric screw 31. (As shown in...) Figure 2 As can be seen, pre-tightening elements 35 are respectively arranged in the annular grooves holding the wiping element 34 or the sealing element 33. The pre-tightening elements 35 are arranged between the sealing element 33 or the wiping element 34 and the bottom of the corresponding groove in the bottom 39 of the volumetric screw, and push the sealing element 33 or the wiping element 34 against the sliding plate 26. Here, the wiping element 34 is used to wipe away the oil accumulated on the sliding plate 26. The sealing element 33 prevents any oil that may not have been wiped away from entering the area filled with compressed air, especially the compression chamber 30.

[0045] Figure 3 A front view of the scroll compressor is shown, particularly the second end cover 6. The first end cover 5 is preferably constructed identically, thereby reducing manufacturing costs.

[0046] End caps 5 and 6 each include a plurality of fastening holes 42, which are regularly arranged on the circumference of end caps 5 and 6. The fastening holes allow end caps 5 and 6 to be fixed to corresponding mating screws 21 and 22, for example by means of screws.

[0047] In addition, each end cover 5, 6 has an air inlet 7 and an air outlet 8. The air inlet 7 is connected to the inlet area of ​​the compression chamber 30. The air outlet 8 is connected to the outlet area of ​​the compression chamber 30. In order to enable water cooling of the scroll compressor, a cooling interface 9 is also provided on the end covers 5, 6. The cooling interface 9 allows a cooling water pump to be connected to form a closed cooling water circuit within the housing 4.

[0048] Figure 4 The scroll compressor is shown along Figure 3 The cross-section of line EE. Therefore, the route of the cross-section is not like, for example, according to Figure 1 The cross-section passes through the scroll compressor in a straight line, just like the cross-section of line EE. Due to the special cutting path along line EE, therefore... Figure 4 The air inlet 7 can also be seen in the area of ​​the first compressor section 2, and according to... Figure 1 The air intake 7 is not visible in the cross-sectional diagram.

[0049] according to Figure 4 The cross-sectional view is intended to illustrate how the two compressor stages, or compressor sections 2 and 3, cooperate with each other. Therefore, it is proposed that the first compressor section 2 pre-compresses the air flowing into the compression chamber 30 of the first compressor section 2 via the inlet 7 in the first end cover 5. The air is first compressed to a moderate air pressure in the first compressor section 2 and then delivered to the compressed air line 40 via the outlet 8 in the first end cover 5.

[0050] The air is intensely heated by compression in the first compressor section 2. To prevent the scroll compressor from overheating, in addition to water cooling via cooling port 9, it is proposed to guide the pre-compressed medium-compressed air through heat exchanger 41. Therefore, heat exchanger 41 is provided in the compressed air line 40, and heat exchanger 41 extracts heat from the medium-compressed air and transfers it to another fluid loop that may be filled with gas or liquid.

[0051] Subsequently, the moderately compressed air cooled in this manner enters the compression chamber 30 of the second compressor section 3 through the air inlet 7 in the second end cover 6. (As in...) Figure 4 As can be seen, the volume of the compression chamber 30 of the second compressor section 3 is smaller than that of the compression chamber 30 of the first compressor section 2, so as to further compress the medium compressed air into high compressed air. The high compressed air leaves the second compressor section 3 through the air outlet 8 in the second end cover 6 (which is preferably connected to the compressed air braking system of the heavy vehicle).

[0052] Specifically, the scroll compressor can be designed to pre-compress air at a pressure of 1 bar at the inlet 7 of the first end cap 5 to a medium air pressure between 3.5 bar and 4 bar in the first compressor stage 2 (first compressor stage), and then post-compress it to a high air pressure of approximately 14 bar in the second compressor stage 3 (second compressor stage). The medium compressed air at a pressure of 3.5 bar to 4 bar is guided via compressed air line 40 to a heat exchanger 41 for cooling before being supplied to the second compressor stage 3 to prevent the second compressor stage 3 from overheating.

[0053] Reference tag list

[0054] 1 drive segment

[0055] 2 First compressor section

[0056] 3 Second compressor section

[0057] 4 housings

[0058] 5 First end cap

[0059] 6 Second end cap

[0060] 7 air intakes

[0061] 8 air outlets

[0062] 9 cooling interfaces

[0063] 10 drives

[0064] 11 electric motors

[0065] 12-axis

[0066] 13 First shaft end

[0067] 14 Second shaft end

[0068] 15 bearings

[0069] 16 eccentric pins

[0070] 17 Eccentric Bearing

[0071] 18 spiral seal

[0072] 19 spiral grooves

[0073] 20 drive housing

[0074] 21 First Paired Spiral

[0075] 22 Second Paired Spiral

[0076] 23 First bearing housing

[0077] 24 Second bearing housing

[0078] 25 guide pins

[0079] 25a anchorage section

[0080] 25b guide section

[0081] 25c protruding shoulders

[0082] 26 sliding plates

[0083] 27 Annular Seal

[0084] 28-Paired Spiral Wall

[0085] 29 Paired Spiral Bottom

[0086] 30 compression chambers

[0087] 31 First volumetric screw component

[0088] 32 Second volumetric screw component

[0089] 33 Sealing elements

[0090] 34 eraser elements

[0091] 35 Preload Components

[0092] 36 sliding elements

[0093] 37 guide ring

[0094] 38 volumetric spiral wall

[0095] 39 Volumetric Spiral Bottom

[0096] 40 Compressed Air Line

[0097] 41 Heat Exchanger

[0098] 42 Fastening holes.

Claims

1. A scroll compressor for generating oil-free compressed air, the scroll compressor having a driver arranged in a housing (4) and connected to a rotating positive displacement screw (31, 32), the positive displacement screw having a positive displacement screw bottom (39) and a positive displacement screw wall (38), wherein, The wall (38) of the volumetric auger is engaged with a fixed pair of augers (21, 22) such that at least one variable compression chamber (30) is formed between the volumetric augers (31, 32) and the pair of augers (21, 22), wherein a sealing element (33) is provided between the volumetric augers (31, 32) and the housing (4), and wherein the sealing element (33) is fastened in the bottom (39) of the volumetric auger and seals relative to a sliding plate (26) which is firmly connected to the housing (4), wherein a wiping element (34) for wiping oil residue off the sliding plate (26) is fastened in the bottom (39) of the volumetric auger.

2. The scroll compressor according to claim 1, characterized in that, The scroll compressor is a scroll compressor used in the compressed air braking system of heavy-duty vehicles.

3. The scroll compressor according to claim 1, characterized in that, The sliding plate (26) has a harder material than the housing (4), at least in the contact area with the sealing element (33).

4. The scroll compressor according to any one of claims 1-3, characterized in that, The bottom (39) of the volumetric spiral has a sealing groove for accommodating the sealing element (33) and / or an erasing groove for accommodating the erasing element (34).

5. The scroll compressor according to any one of claims 1-3, characterized in that, The sliding element (36) is arranged between the volumetric screw (31, 32) and the sliding plate (26).

6. The scroll compressor according to claim 4, characterized in that, The sliding element (36) is arranged between the volumetric screw (31, 32) and the sliding plate (26).

7. The scroll compressor according to claim 5, characterized in that, The sliding element (36) is radially arranged within the sealing element (33) and / or the wiping element (34).

8. The scroll compressor according to claim 6, characterized in that, The sliding element (36) is radially arranged within the sealing element (33) and / or the wiping element (34).

9. The scroll compressor according to any one of claims 1-3 and 6-8, characterized in that, Guide pins (25) are anchored in the housing (4) and extend through an opening in the sliding plate (26) to guide rings (37) arranged in the bottom (39) of the volumetric screw, wherein each guide pin (25) has a shoulder (25c) protruding beyond the sliding plate (26) such that there is a gap between the respective guide ring (37) and the sliding plate (26).

10. The scroll compressor according to claim 4, characterized in that, Guide pins (25) are anchored in the housing (4) and extend through an opening in the sliding plate (26) to guide rings (37) arranged in the bottom (39) of the volumetric screw, wherein each guide pin (25) has a shoulder (25c) protruding beyond the sliding plate (26) such that there is a gap between the respective guide ring (37) and the sliding plate (26).

11. The scroll compressor according to claim 5, characterized in that, Guide pins (25) are anchored in the housing (4) and extend through an opening in the sliding plate (26) to guide rings (37) arranged in the bottom (39) of the volumetric screw, wherein each guide pin (25) has a shoulder (25c) protruding beyond the sliding plate (26) such that there is a gap between the respective guide ring (37) and the sliding plate (26).

12. The scroll compressor according to any one of claims 1-3, 6-8 and 10-11, characterized in that, The actuator is arranged between the first volumetric screw (31) and the second volumetric screw (32).

13. The scroll compressor according to claim 4, characterized in that, The actuator is arranged between the first volumetric screw (31) and the second volumetric screw (32).

14. The scroll compressor according to claim 5, characterized in that, The actuator is arranged between the first volumetric screw (31) and the second volumetric screw (32).

15. The scroll compressor according to claim 9, characterized in that, The actuator is arranged between the first volumetric screw (31) and the second volumetric screw (32).

16. The scroll compressor according to claim 12, characterized in that, The driver has a shaft (12) with two shaft ends (13, 14), wherein the first shaft end (13) is connected to the first volumetric screw (31) and the second shaft end (14) is connected to the second volumetric screw (32).

17. The scroll compressor according to any one of claims 13-15, characterized in that, The driver has a shaft (12) with two shaft ends (13, 14), wherein the first shaft end (13) is connected to the first volumetric screw (31) and the second shaft end (14) is connected to the second volumetric screw (32).

18. The scroll compressor according to claim 12, characterized in that, The first volumetric screw (31) and the first paired screw (21) form a first compressor stage, and the second volumetric screw (32) and the second paired screw (22) form a second compressor stage.

19. The scroll compressor according to claim 17, characterized in that, The first volumetric screw (31) and the first paired screw (21) form a first compressor stage, and the second volumetric screw (32) and the second paired screw (22) form a second compressor stage.

20. The scroll compressor according to any one of claims 13-16, characterized in that, The first volumetric screw (31) and the first paired screw (21) form a first compressor stage, and the second volumetric screw (32) and the second paired screw (22) form a second compressor stage.

21. The scroll compressor according to any one of claims 1-3, 6-8, 10-11, 13-16, and 18-19, characterized in that, A spiral seal (18) is provided between the volumetric spiral wall (38) and the mating spiral (21, 22) and between the mating spiral wall (28) and the volumetric spiral (31, 32).

22. The scroll compressor according to claim 4, characterized in that, A spiral seal (18) is provided between the volumetric spiral wall (38) and the mating spiral (21, 22) and between the mating spiral wall (28) and the volumetric spiral (31, 32).

23. The scroll compressor according to claim 5, characterized in that, A spiral seal (18) is provided between the volumetric spiral wall (38) and the mating spiral (21, 22) and between the mating spiral wall (28) and the volumetric spiral (31, 32).

24. The scroll compressor according to claim 9, characterized in that, A spiral seal (18) is provided between the volumetric spiral wall (38) and the mating spiral (21, 22) and between the mating spiral wall (28) and the volumetric spiral (31, 32).

25. The scroll compressor according to claim 12, characterized in that, A spiral seal (18) is provided between the volumetric spiral wall (38) and the mating spiral (21, 22) and between the mating spiral wall (28) and the volumetric spiral (31, 32).

26. The scroll compressor according to claim 17, characterized in that, A spiral seal (18) is provided between the volumetric spiral wall (38) and the mating spiral (21, 22) and between the mating spiral wall (28) and the volumetric spiral (31, 32).

27. The scroll compressor according to claim 20, characterized in that, A spiral seal (18) is provided between the volumetric spiral wall (38) and the mating spiral (21, 22) and between the mating spiral wall (28) and the volumetric spiral (31, 32).

28. The scroll compressor according to claim 21, characterized in that, The first spiral seal (18) is arranged in the spiral groove (19) of the volumetric spiral wall (38) which is open toward the paired spirals (21, 22), and the second spiral seal (18) is arranged in the spiral groove (19) of the paired spiral wall (28) which is open toward the volumetric spirals (31, 32).

29. The scroll compressor according to any one of claims 22-27, characterized in that, The first spiral seal (18) is arranged in the spiral groove (19) of the volumetric spiral wall (38) which is open toward the paired spirals (21, 22), and the second spiral seal (18) is arranged in the spiral groove (19) of the paired spiral wall (28) which is open toward the volumetric spirals (31, 32).

30. The scroll compressor according to any one of claims 1-3, 6-8, 10-11, 13-16, 18-19 and 22-28, characterized in that, The driver and / or the housing (4) and / or the mating screws (21, 22) are water-cooled.

31. The scroll compressor according to claim 4, characterized in that, The driver and / or the housing (4) and / or the mating screws (21, 22) are water-cooled.

32. The scroll compressor according to claim 5, characterized in that, The driver and / or the housing (4) and / or the mating screws (21, 22) are water-cooled.

33. The scroll compressor according to claim 9, characterized in that, The driver and / or the housing (4) and / or the mating screws (21, 22) are water-cooled.

34. The scroll compressor according to claim 12, characterized in that, The driver and / or the housing (4) and / or the mating screws (21, 22) are water-cooled.

35. The scroll compressor according to claim 17, characterized in that, The driver and / or the housing (4) and / or the mating screws (21, 22) are water-cooled.

36. The scroll compressor according to claim 20, characterized in that, The driver and / or the housing (4) and / or the mating screws (21, 22) are water-cooled.

37. The scroll compressor according to claim 21, characterized in that, The driver and / or the housing (4) and / or the mating screws (21, 22) are water-cooled.

38. The scroll compressor according to claim 29, characterized in that, The driver and / or the housing (4) and / or the mating screws (21, 22) are water-cooled.

39. A compressed air braking system comprising a scroll compressor according to any one of claims 1-38.

40. The compressed air braking system according to claim 39, characterized in that, The compressed air braking system is a compressed air braking system for heavy-duty vehicles.

Images