SCREW COMPRESSOR ELEMENT AND MACHINE

Abstract

Screw compressor element provided with a housing wherein a rotor is rotatably arranged by way of two bearings, respectively being a cylinder bearing (3) and a ball bearing (4), each provided with an inner ring (5, 6) and an outer ring (7, 8), separated by respectively cylindrical, or ball-shaped rolling elements (9, 10) that contact the inner ring (5, 6) and the outer ring (7, 8) at the location of a raceway (11a, 11b, 12a, 12b), characterised in that, next to the respective raceway (11a, 12a), the inner rings (5, 6) of the aforementioned bearings (3, 4) have a smaller outer diameter (B) than the respective raceway (11a, 12a) on the side facing the other bearing (3, 4) and in that next; to the respective raceway (11a, 12a), the inner rings (5, 6) of the bearings have a greater outer diameter (C, D) than the respective raceway (11a, 11b) on the side facing away from the other bearing (3, 4).

Claims

1-36. (canceled)

37. A screw compressor clement provided with a housing wherein a rotor is rotatably arranged by way of two bearings, respectively being a cylinder bearing (3) and a ball bearing (4), each provided with an inner ring (5,6) and an outer ring (7, 8), separated by respectively cylindrical, or ball-shaped rolling elements (9, 10) that contact the inner ring (5, 6) and the outer ring (7, 8) at the location of a 10 raceway (11a, 11b, 12a, 12b), characterized in that next to the respective raceway (11a, 12a), the inner rings (5, 6) of the aforementioned bearings (3, 4) have a smaller outer diameter (B) than the respective raceway (11a, 12a) on the side facing the other bearing (3, 4) and in that next to the respective raceway (11a, 12a), the inner rings (5, 6) of the bearings have a greater outer diameter (C, D) than the respective raceway (11a, 11b) on the side facing away from the other bearing (3, 4), and wherein next to the respective raceway (11b, 12b), the outer rings (7, 8) of the bearings (3, 20 4) have a smaller inner diameter (D, G) than the respective raceway (11b, 12b) both on the side facing the other bearing (3, 4) and on the side facing away from the other bearing (3, 4).

38. A screw compressor element provided with a housing wherein a rotor is rotatably arranged by way of two bearings, respectively being a cylinder bearing (3) and a ball bearing (4), each provided with an inner ring (5, 6) and an outer ring (7, 8), separated by respectively cylindrical, or ball-shaped rolling elements (9, 10) that contact the inner ring (5, 6) and the outer ring (7, 8) at the location of a raceway (11a, 11b, 12a, 12b), wherein next to the respective raceway (11a, 12a), the inner rings (5, 6) of the aforementioned bearings (3, 4) have a smaller outer diameter (B) than the respective raceway (11a, 12a) on the side facing away from the other bearing (3, 4) and in that next to the respective raceway (11a, 12a), the inner rings (5, 6) of the bearings have a greater outer diameter (C, D) than the respective raceway (11a, 11b) on the side facing the other bearing (3, 4), wherein next to the respective raceway (11b, 12b), the outer rings (7, 8) of the bearings (3, 4) have a smaller inner diameter (D, G) than the respective raceway (11b, 12b) both on the side facing the other bearing (3, 4) and on the side facing away from the other bearing (3, 4).

39. The screw compressor element according to claim 37, wherein the inner diameters (A) of the inner rings (5, 6) of the cylinder bearing (3) and of the ball bearing (4) are identical.

40. The screw compressor element according to claim 37, wherein at least one nozzle (19) is arranged between the cylinder bearing (3) and the ball bearing (4), this nozzle (19) being suitable for spraying a fluid into the cylinder bearing (3) and/or into the ball bearing (4).

41. The screw compressor element according to claim 37, wherein at least one nozzle (19) is arranged between the cylinder bearing (3) and the ball bearing (4), this nozzle (19) being suitable for spraying a fluid in between the basket of the cylinder bearing (3) and the inner ring (5) and/or in between the basket of the ball bearing (4) and the inner ring (6).

42. The screw compressor element according to claim 37, wherein the cylinder bearing (3) is provided with two fixed collars (13) on the outer ring (7) and one fixed collar (14) on the inner ring (5), or in that the cylinder bearing (3) is provided with two fixed collars (13) on the outer ring (7) and one loose collar (14) on the inner ring (7), or in that the cylinder bearing (3) is provided with two fixed collars (13) on the outer ring (7) and one hook ring on the inner ring (5).

43. The screw compressor element according to claim 37, wherein the difference between the diameter (E) of the rolling elements (9) of the cylinder bearing (3) and the diameter (F) of the rolling elements (10) of the ball bearing (4) is not greater than 20%, preferably not greater than 10%, and yet preferably not greater than 5%.

44. The screw compressor element according to claim 37, wherein at least one of the rolling elements (9, 10) of the cylinder bearing (3) and/or the ball bearing (4) is made out of a ceramic material.

45. The screw compressor element according to claim 44, wherein all the rolling elements (9, 10) of the cylinder bearing (3) and/or ball bearing (4) are made out of a ceramic material.

46. The screw compressor element according to claim 37, wherein the cylinder bearing (3) and/or the ball bearing (4) are provided with a basket made out of a polymer.

47. The screw compressor element according to claim 46, wherein the polymer is fiber-reinforced.

48. The screw compressor element according to claim 37, wherein the outer ring (8) of the ball bearing (4) is provided with two raceways (12b, 12c).

49. The screw compressor element according to claim 48, wherein the contact angles on the two raceways (12b, 12c) of the outer ring (8) of the ball bearing (4) are different.

50. The screw compressor element according to claim 37, wherein the bearings (3, 4) are suitable for being used at speeds higher than 1*106 ndm [millimeters×revolutions per minute], preferably higher than 1.25*106 ndm, and yet preferably higher than 1.5*106 ndm.

51. A machine comprising the screw compressor element according to claim 37, wherein the machine is one of the group of: a compressor, preferably an oil-free compressor; a blower, preferably an oil-free blower; an expander, preferably an oil-free expander; a vacuum pump, preferably an oil-free vacuum pump.

Description

[0058] In order to better demonstrate the features of the invention, some preferred embodiments are described hereinafter, in an exemplary manner and without any restrictive character, of a screw compressor element and of a machine according to the invention, with reference to the accompanying drawings, wherein

[0059] FIG. 1 is a schematic representation of a part of a screw compressor element according to prior art;

[0060] FIG. 2 is a schematic representation of a screw compressor according to the invention; and

[0061] FIG. 3 is a schematic representation of the part that is marked in FIG. 2 with reference marker F3.

[0062] The set of bearings 1 in a screw compressor element according to prior art as shown in FIG. 1 relates to a fixed set of bearings 1, mounted on a shaft 2. The set of bearings 1 contains two bearings 3, 4: a cylinder bearing 3 and a ball bearing 4.

[0063] Each bearing 3, 4 has an inner ring 5, 6 and an outer ring 7, 8, with cylindrical rolling elements 9 or ball-shaped rolling elements 10 between them, respectively.

[0064] The rolling elements 9, 10 contact the inner ring 5, 6 and the outer ring 7, 8 at the location of the raceway 11a, 11b, 12a, 12b.

[0065] As shown in FIG. 1, the nominal inner diameters A of the inner rings 5, 6 are equal. This means that the ‘bore hole’ of the inner rings 5, 6, i.e. the opening used to arrange the bearings 3, 4 on a shaft 2, is identical.

[0066] The cylinder bearing 3 is a bearing of the NJ type: the outer ring 7 is provided with two collars 13; the inner ring 5 is provided with one collar 14.

[0067] As shown in FIG. 1, the collar 14 on the inner ring 5 faces away from the ball bearing 4.

[0068] By using an NJ bearing, the inner ring 5 has a smaller outer diameter B next to the raceway 11a on the side facing the ball bearing 4, and a larger outer diameter C next to the raceway 11a on the other side.

[0069] Next to the raceway 11b, the outer ring 7 of the cylinder bearing 3 also has on both sides of the raceway 11b a smaller inner diameter D than the raceway 11b, because the outer ring 7 is provided with two collars 13.

[0070] The ball bearing 4 in this case is an angular contact bearing, wherein next to the raceway 12a, on the side facing the cylinder bearing 3, the inner ring 6 has a smaller outer diameter B than the raceway 12a on the inner ring 6.

[0071] In other words: the inner ring 6 of the ball bearing 4 has no ‘edge’ on the side of the cylinder bearing 3.

[0072] Next to the raceway 12a, on the side facing away from the cylinder bearing 3, the inner ring 6 has a larger outer diameter G than the raceway 12a on the inner ring 6.

[0073] FIG. 2 is a schematic representation of a screw compressor element 15 according to the invention.

[0074] The screw compressor element 15 is provided with a housing 16, in which a rotor 17 is rotatably arranged. In this case, two such rotors 17 are arranged, but this is not necessary in terms of the invention.

[0075] The rotors 17 are borne by way of their shaft 18 by bearings 3, 4 in the housing 16.

[0076] Even though in the example shown, both ends of the shaft 18 of both rotors 17 are borne by way of two bearings 3, 4 in the housing 16, it is also possible that only one end of the shaft 18 or only one of the two rotors 17 is borne with two bearings 3, 4 in the housing 16.

[0077] FIG. 3 shows a part of the screw compressor element 15 according to the invention from FIG. 2, and more specifically an end of a shaft 18 of one of the rotors 17 with the two bearings 3, 4. As is clearly visible in this detail figure, the one bearing 3 is a cylinder bearing, and the other bearing 4 is a ball bearing.

[0078] In the shown example, the cylinder bearing 3 is the same as in FIG. 1, but for this cylinder bearing 3, for instance, the following types may be used: [0079] an NJ bearing as shown in FIG. 1, in which the cylinder bearing 3 has two fixed collars 13 on the outer ring 7 and one fixed collar 14 on the inner ring 5; [0080] an NJP bearing, in which the cylinder bearing 3 has two fixed collars 13 on the outer ring 7 and one loose collar 14 on the inner ring 5; or [0081] an NU bearing with an angle ring, in which the cylinder bearing 3 has two fixed collars 13 on the outer ring 7 and an angle ring on the inner ring 5.

[0082] The ball bearing 4 is different from the one in the configuration shown in FIG. 1. In this case, the ball bearing 4 is a three-point bearing, more specifically a bearing that has two raceways 12b and 12c on the outer ring 8 and one raceway 12a on the inner ring 6. The ball bearing 4 is therefore not an angular contact ball bearing.

[0083] An example of a suitable ball bearing 4 is described, for instance, in US 2016/0312823 A1 in the name of Aktiebolaget SKF. The description of this American patent application according to paragraphs [0022] to [0038] of US 2016/0312823 A1 is integrally incorporated by reference in the present application.

[0084] Alternatively, the ball bearing 4 may consist of a four-point bearing, of which the inner ring 6 as well as the outer ring 8 have two raceways 12a, 12b, 12c.

[0085] In this case, though not necessarily, the contact angles of the two raceways 12b and 12c are different.

[0086] Whenever the speed increases, the rolling elements 10 will experience an outward radial centrifugal force. This will involve a certain axial displacement.

[0087] Due to the presence of the second raceway 12c, the rolling elements 10 will roll on the second raceway 12c at high speeds, and the aforementioned axial displacement will be reduced to a minimum.

[0088] This will ensure that the set of bearings 1 can function optimally despite the high speeds. Furthermore, the axial displacement of the rotor on which the set of bearings 1 is positioned as a fixed bearing will be limited, such that there will be little or no increase of the play at the tip, and therefore little or no extra losses in the screw compressor due to leakages.

[0089] Furthermore, next to the raceways 12b, 12c, on the side facing the cylinder bearing 3 as well as on the side facing away from the cylinder bearing 3, the outer ring 8 of the ball bearing 4 has a smaller inner diameter G than the raceways 12b, 12c.

[0090] The diameter E of the cylindrical rolling elements 9 is equal in this case to the diameter F of the bail-shaped rolling elements 10.

[0091] Because both types of rolling elements 9, 10 are made of the same material, the centrifugal forces will be of a similar magnitude.

[0092] However, a difference in diameter E, F between the rolling elements 9, 10 of the two bearings 3, 4 cannot be ruled out. This difference is preferably less than 20%, more preferably less than 10% and most preferably not greater than 5%, such that the difference in the centrifugal forces can be limited in as much as possible.

[0093] Even though FIG. 3 does not show a bearing cage, it can obviously not be excluded that one or both of the two bearings 3, 4 has a bearing cage.

[0094] As shown in FIG. 3, a nozzle 19 is arranged between the ball bearing 4 and the cylinder bearing 3.

[0095] This nozzle 19 can direct jets 20 of lubrication fluid into the cylinder bearing 3 and/or the ball bearing 4.

[0096] In this case, the nozzle 19 will direct two jets 20 of fluid, one at the cylinder bearing 3 and one at the ball bearing 4, respectively.

[0097] For these purposes, the nozzle 19 has two openings 21.

[0098] It is obviously also possible that two nozzles 19 are provided: one for the cylinder bearing 3, and one for the ball bearing 4. However, in this case, one nozzle 19 is enough.

[0099] In this case, the nozzle 19 directs a jet 20 of oil at the bearings 3, 4. It can obviously not be ruled out that another liquid be used, for instance water.

[0100] If one or both bearings 3, 4 are provided with a bearing cage, preferably, at least one nozzle 19 is arranged between the cylinder bearing 3 and the ball bearing 4, wherein the nozzle 19 is suited for aiming a jet 20 of lubrication fluid between the cage of the cylinder bearing 3 and the inner ring 5, and/or between the cage of the ball bearing 4 and the inner ring 6, such that a big part of the lubrication fluid ends up on raceways, preferably on the raceways 11a, 12a of the inner rings 5, 6.

[0101] The bearings 3 and 4 from FIG. 3, and by extension, any set of bearings 1 according to the invention, are suited for being used at speeds higher than 1*10.sup.6 nd.sub.m [millimeter×revolutions per minute], preferably higher than 1.25*10.sup.6 nd.sub.m, and more preferably higher than 1.5*10.sup.6 nd.sub.m.

[0102] Due to the specific features of a set of bearings 1 according to the invention, the disadvantages of the known sets of bearings at high speeds will not occur, such that the set of bearings 1 may be used at such high speeds.

[0103] For further clarification: Some additional explanations are given below of the type of bearing that can be used as a ball bearing 4 in a screw compressor element 15 or in another machine according to the invention. This explanation is taken from US 2016/0312823 A1 in order to make it possible to include features such as those described therein in the claims of the present patent application, to the extent that such should turn out to be necessary in light of earlier publications of which the applicants are currently still unaware. After all, it was demonstrated that the specific application of a three-point bearing as described in US 2016/0312823 A1 leads to surprisingly good results in the specific application of a screw compressor element 15.

[0104] It is clear that the scope of protection of the present invention is not limited to this specific configuration, but rather, that it should be considered a preferred embodiment.

[0105] A preferred roller bearing 4 comprises an outer ring and an inner ring. Between the inner ring and the outer ring, a number of rolling elements are arranged. The outer ring contains at least one raceway for rolling elements more than the inner ring. The roiling elements are arranged in a single row, they are embodied as balls and are preferably encased in a cage. In one embodiment, the outer ring contains an additional and/or second raceway on a radially inwards-facing surface on which the first raceway is arranged as well. The two raceways of the outer ring are preferably symmetrical with respect to each other. The outer ring may be embodied as the conventional outer ring of a four-point bearing or as an outer ring of a similar design. In a preferred embodiment, the inner ring comprises exactly one raceway. The raceway of the inner ring is preferably arranged diagonally with respect to the first raceway of the outer ring. The inner ring is arranged concentrically within the outer ring.

[0106] The outer ring may be provided with two circular arc segments on its radially inward-facing surface, each of these arc segments comprising one of the raceways of the outer ring. A curvature radius of the circular arc segments may, for instance, be larger than a factor 1.01; 1.02; 1.03; 1.04; 1.05; 1.06; 1.07; 1.08; 1.09, or 1.20 than a jet of the rolling element. At one point, the aforementioned radially inward facing surface may have a curve or a discontinuity, such that during operation, the rolling elements run only on the two raceways and have no further contact with that surface. This point may be, for instance, at the radially outermost position.

[0107] The two raceways on the outer ring may be spaced axially at a distance from each other, this distance being larger than zero. The raceways preferably extend along the entire outer ring in the circumferential direction.

[0108] Even though all the variants of the invention shown and described above feature a compressor element 15, it is not excluded that the invention relates to a different machine, wherein this machine is provided with a housing in which a rotor is rotatably arranged by way of two bearings 3, 4, respectively a cylinder bearing 3 and a ball bearing 4.

[0109] This machine may be an oil-free screw compressor, blower, expander, or vacuum pump.

[0110] The aforementioned oil-free screw compressor comprises one or more of the compressor elements 15 shown and described above.

[0111] It is possible that in all the variants shown and described above, the bearings 3, 4 have mutually switched positions, such that collars or ‘edges’ are now located next to the raceways 11a, 12a on the inner bearing rings 5, 6 on the inward-facing side of the bearings 3, 4.

[0112] This means that the bearings 3, 4 have collars or ‘edges’ next to the raceways 11a, 12a on the inner bearing rings 5, 6 that are facing each other, such that next to the respective raceway 11a, 12a, the inner rings 5, 6 of the aforementioned bearings 3, 4 have a smaller outer diameter B than the respective raceway 11a, 12a on the side facing away from the other bearing 3, 4 and in that next to the respective raceway 11a, 12a, the inner rings 5, 6 of the bearings have a greater outer diameter C, D than the respective raceway 11a, 11b on the side facing the other bearing 3, 4.

[0113] Thus, the bearings will be positioned ‘back-to-back’ rather than ‘face-to-face’, as in FIG. 3.

[0114] In such a ‘back-to-back’ configuration of the bearings 3, 4, preferably, two nozzles 19 are used, on either side of the set of bearings 1.

[0115] Thus, the nozzles 19 can inject a fluid on the side of the bearings 3, 4 on which the inner ring 5, 6 has no collar or ‘edge’.

[0116] The present invention is in no way limited to the embodiments described in the examples and shown in the figures, but a machine and/or a screw compressor element according to the invention may be realized in a variety of forms and dimensions without falling outside the scope of the invention.