JPH04501901A - vane compressor - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

[Detailed description of the invention] vane compressor technical situation The invention relates to a vane compressor of the type specified by the generic part of claim 1. or relating to vane compressors.

A device of this type already known from German Patent Application No. 2223156 In a vane compressor, the inlet opening of each low pressure chamber extends along the entire length of the rotor. are distributed and spaced axially from each other into axial supply passages. Due to the connection, the cooling medium flows radially into the low pressure chamber. one end face The supply channel, which is closed on one side, is connected to the drive shaft in the casing cutout on the other end side. extends beyond the boundary wall located near () where it opens into an annular chamber, which is Connected to a radial connecting pipe section provided for the return flow of cooling medium from the device. Ru. Therefore, the expanded, cooled, and oil-rich cooling medium flows in. The front part of the casing and rotor near the drive shaft is the rear part away from the drive shaft. Cools more strongly than other parts. There is also uneven temperature around the casing and rotor. Degree distribution occurs. As shown by experiments, this strongly non-uniform temperature distribution This is often the cause of failures in this type of vane compressor.

Furthermore, in this known vane compressor the oil is separated from the cooling medium on the pressure side. , this high-pressure oil is used as a sealing means supplied through the sideways boundary wall. . For this purpose, a recess is provided in the boundary wall. The notch is used for oil separator. It is connected to a hole that opens into an oil storage chamber supplied by the oil tank. Occurs in the oil storage room The high pressure forces the oil into the holes, from where it passes through the notches to the end of the rotor. It is guided between the surface and the boundary wall surface next to it. In the sealing action of oil under high pressure, high pressure The oil temperature is only slightly higher than the temperature of the cooling medium below, that is, the so-called hot gas temperature. The viscosity of the oil is relatively low and it can no longer absorb heat. I have to accept the disadvantage of not being able to do it.

In addition, this high-temperature oil flows between the bottom surface of the guide groove and the vane guide slit of the rotor. By flowing into the lower surface of the vane into the hollow chamber partitioned by the It also gets relatively hot6 Advantages of invention The vane type compressor according to the present invention having the features set forth in the characteristic part of claim 1 is as described above. cooling medium from a separate supply chamber located coaxially with the rotor axis. A similar feed path is created by feeding the casing, which results in a nearly uniform The entire central part of the casing surrounding the zero rotor has the advantage of providing high heating. Evenly distributing heat across the chamber means that the cooling medium at approximately the same temperature is Zero rotor front end and rear end achieved by feeding axially on the side The temperature at the ends is kept at the same level by the above, and towards the center of the rotor the temperature decreases. It will rise only slightly.

A generally approximately uniform temperature distribution is achieved throughout the vane compressor.

Depending on the exit described in claim 2 and subsequent claims, the vane compressor according to claim 1 can be It can be developed and improved with advantage.

According to an advantageous embodiment of the invention with a hollow rotor shaft, there is a Each connection is made in front of the rotor end face, so that the cooling medium from the device is The return conduit can be connected to the center of one supply chamber. In this case, The flow of the cooling medium is directed into the first supply chamber and into a supply passage extending partially therefrom. A portion is distributed through the hollow rotor shaft to the other supply chamber. second supply The flow of the cooling medium in the chamber is further extended to a supply passage branching from there. divided into sub-streams to feed the body. As a result, this Not only is it easy to allow the cooling medium to flow through the shaft, but the shaft seal is also It becomes loaded only by force and lower temperature.

Separation of oil takes place by dividing and deflecting the cooling medium into separate sub-streams 0 According to another implementation of the invention 11141, the flow of the cooling medium is divided in the first supply chamber. Due to the weir pressure generated when cracking, the oil-rich cooling medium is cooled by appropriate means. Hollow chamber of the vane guide slit partitioned by the slit bottom and the vane bottom The vanes are guided through the vane guide slits while passing through the high pressure chamber by suitable means. When the coolant in the hollow chamber is forced into the rotor, the coolant in the hollow chamber is Not only can it flow out, but also the lubrication and sealing effects are well achieved. In addition, the frictional heat on the vane end surface is absorbed by low-temperature oil. low pressure chamber and The seal between the high pressure chamber is achieved by a cooler and therefore more viscous oil. As a result, the temperature level within the vane compressor is generally relatively low.

Suitable means for supplying oil to the hollow space in the vane guide slit can be used in other embodiments of the invention. According to an aspect, the boundary wall located immediately next to the first supply chamber, facing the rotor, An arc-shaped recess is provided on the end surface, and the recess penetrates the boundary wall and is provided approximately in the axial direction. It communicates with the first supply chamber through a hole in which the vane passes through the low pressure area. , each communicating with a hollow chamber in the vane guide slit.

Suitable for pushing out the oil-rich cooling medium in the hollow chamber of the vane guide slit. The means, according to another embodiment of the invention, are as follows. In other words, the boundary Arc-shaped grooves are provided on both end faces of the parting wall facing the rotor, and the vanes are raised high. During passage through the pressure zone, each line groove communicates with a hollow chamber in the vane guide slit. It looks like this.

Communicating the arc-shaped recess or groove with the hollow chamber of the vane guide slit is According to a preferred embodiment, this is advantageously realized in the following manner. That is, The recess or groove in question, which has a slight width in the radial direction, has its central longitudinal edge. is located on a rotating orbit extending from the bottom of the vane guide slit, extending over at least one partial region of the low-pressure chamber or the high-pressure chamber, viewed in the circumferential direction; ing.

drawing Hereinafter, the present invention will be described in detail based on embodiments shown in the drawings.

Figure 1 is a longitudinal sectional view of a vane compressor, and Figure 2 is taken along line H-■ in Figure 1. FIG.

Description of examples The vane compressor shown in the longitudinal cross-sectional view in Figure 1 and the cross-sectional view in Figure A vane-type or vane-type compressor consists essentially of three parts: a left-hand end cover; 1, a right end surface [12, and a casing center portion 13] It has 10. The casing central part 13 has a casing cutout 14 inside. It is. The axially lateral boundary walls 15.16 of the housing recess 14 are , formed by end caps 11.12. As seen in Figure 2, the casing The inner wall surface 17 of the central portion 13 of the vane compressor is an ellipse that also forms the stroke curved surface of the vane compressor. It has a shaped curved surface.

A cylindrical rotor 18 is provided in the casing interior 14, and the rotor is directly connected to the rotor. The diameter is equivalent to the length of the smaller axis of the ellipse above, excluding a slight rotational play. Ru. In this way, the circumferential surface 19 of the rotor 18 and the inner wall surface 1 of the casing central portion 13 are 7 and the length of the rotor 18 between which two crescent-shaped working chambers 21 and 22 are formed. The rotor has slight play along the boundary walls 15.16 of the end caps 11.12 at both ends. It was chosen so that it could be rotated without putting anything on it.

The rotor 18 is arranged on the rotor shaft 20, and in this embodiment, the rotor 18 is arranged on the rotor shaft 20. The child shaft 20 is constructed integrally with the rotor 18.The first rotor shaft 20 has both end surfaces l[11, The rotor shaft 20 is supported by two needle bearings 23 and 24 provided in the rotor shaft 12. One end, the left end in FIG. 1, is fixed to the drive shaft 25 in a relatively non-rotatable manner. Drive The rotor shaft 20 and, in turn, the rotor 18 are rotated by the dynamic shaft 25 . end cover 11 and the drive shaft 25 is a seal 26 which serves for a radial sealing action. ing.

In the rotor 18 there are a plurality of slits 27, here five, running approximately radially. A vane 28 is provided in each slit in a tight and sliding manner. You will be guided to do so. The vane 28 is attached at the outer edge 29 to the casing central part 13. The working chamber 21, 22 is divided into independent chambers. Crescent Moon Each of the two shaped working chambers 21.22 has a suction chamber or low pressure chamber 30.3. 1 and high pressure chambers 32 and 33. Each low pressure chamber faces each other In a drawing with two inflow openings on the end faces, the inflow openings are Inlet openings 34 provided in both lateral boundary walls 15.16 of the lid 11.12 ．． 35 (Fig. 1) and can also be seen as inlet openings 35, 36 (Fig. 2). Ru. Each boundary wall 15 or 16 therefore has two inlet openings 3 respectively. 5 and 36 or 34 will be present. The inflow openings 34 to 36 are This serves as an opening for a supply passage running through the end surface 1 [11, 12]. The supply passage is the first In the figure, the supply passages are shown as 38, 39, 40.

It leads to an inlet opening 34 or 35 and 36 on the boundary wall 15 or 16. The supply passages 38 or 39,40, respectively, are coaxial supply passages with respect to the rotor shaft 20. It opens into chamber 41 or 42. In this case, the supply passage 38 or 39.4 0 diverge approximately radially from the associated supply chamber 41 or 42. same supply All supply passages 38 or 39, 40 opening into chambers 41 or 42 are It extends symmetrically around the rotor axis through the end covers 11 and 12, and thus extends in the same direction. have the same length. The first supply chamber 42 provided in the right end cover 12 is On one side, it is arranged to be partially restricted by the free end of the rotor shaft 20. Ru. The supply chamber 42 connects directly to the coolant return conduit represented by arrow 43 in FIG. It is connected. The expanded and recooled cooling medium returning from the equipment is direction, it flows into the first supply chamber 42 . A second supply provided in the left end cover 11 The feed chamber 41 is formed as an annular chamber and surrounds the rotor shaft 20. 20 has a blind hole 44 that reaches as far as the second supply chamber 41; 4 is a blind hole 4 that opens into the first supply chamber 42 at the free end of the rotor shaft 20. Through a radial hole 45 that intersects the rotor shaft 20 and passes through the rotor shaft 20, the blind hole 44 It communicates with the supply chamber 41 of No. 2.

Each high pressure chamber 32,33 has a radial inflow opening 46 or 47 (FIG. 2). through which it communicates with pressure passage 48 or 49. Outflow openings 46.47.

In the illustrated embodiment, it is configured as a tongue-shaped valve, which is only schematically illustrated in the drawing. Although not shown in detail in the drawing, both pressure passages have outflow valves 51, 52. 48, 49 lead to one common collecting chamber 53 (FIG. 1), which is connected to a pressure connection pipe. It communicates with section 54. The cooling medium compressed through the pressure connecting pipe section 54 is to the device, as represented by arrow 55 in FIG.

For sealing and lubrication of rotor 18 and vanes 28, supply passages 39,40 and By effectively utilizing the weir pressure generated when the cooling medium flows into the blind hole 44, a small amount of cooling medium is of cooling medium is present in the vane guide slit 27 from the first supply chamber 42 and flows through the slit. It flows directly into a hollow chamber 56 partitioned by a vane bottom surface 57 and a vane bottom surface 58.

This filling of the hollow chamber 56 is caused by the passage of the individual vanes through the low pressure chamber 30. It happens all the time. Meanwhile, the volume of the hollow chamber 56 increases as the vanes 28 move outward from the center. It is expanded by slipping out. For this purpose, the border of the right end cover 12 must be Arc-shaped recesses 59 and 60 are provided on the wall surface 16 with a slight width in the radial direction. It is. The recesses 59,60 are depicted in broken lines in FIG. The recess is inside With the central longitudinal edges 61, 62, the slit bottom of the vane guide slit 27 It is located on a rotating orbit extending from the surface 57 and covers all of the low pressure chambers 30 and 31 when viewed in the circumferential direction. covering an area or part of an area.

Each recess 59,60 is connected through a bore 63,64 running generally axially in the end face 112. and communicates with the first supply chamber 42 . In this way, the vane 28 is placed in the low pressure chamber. 30.31, the hollow chamber 56 in the vane guide slit 27 is filled with the recess 5. Connects with 9.60. Therefore, due to the weir pressure in the first supply chamber 42, the holes 63, 64 and the oil-rich cooling medium cooled through the recess 59,60 in the hollow chamber 5 Pushed into 6.

While the vane 28 passes through the high pressure chamber 32, 33, the vane 28 slides into the vane guide slit. The volume of the hollow chamber 56 is the same as that of the high pressure chamber 32.33. It decreases to its minimum at the edge. The cooling medium in the hollow chamber 56 was removed from both end covers 11 and 12. The rotor is pushed out into an arcuate groove on both boundary walls 15 and 16 of the Along the end face of 18 and the end face l [boundary wall surfaces 15 and 16 of 11 and 12, both working chambers 2 1.22 Go inside. The cooling medium exerts a sealing and lubricating effect between the above surfaces. .

A small amount of cooling medium flows from the hollow chamber 56 directly along the vane surface into the working chamber 21.2. 2 Go inside. This cooling medium also exhibits sealing, lubricating, and cooling effects. The groove In FIG. 2, the grooves 65 and 66 on the boundary wall surface 16 of the end cover 12 on the right side are indicated by broken lines. This is a drawing. The line groove is attached to the base with its central longitudinal edge 67 or 68. located substantially on the rotational track extending from the slit bottom surface 57 of the horn guide slit 27, Viewed in the circumferential direction, they each cover the entire area or part of the high pressure chamber 32,33.

The line grooves 65,66, like the recesses 59,60, have a small width in the radial direction.

The present invention relates to the vane compressor shown in the drawings having a casing cutout 14 having an oval cross section. The invention is limited to a casing having a cylindrical rotor. The same applies to a single-flow vane compressor that is eccentrically placed in a notch. It can be implemented with advantage.

Fig, 2 international search report international search report PCT/DE 89100717

Claims (1)

[Claims] 1. It has a cylindrical rotor installed in the casing notch, and the rotor located on a rotor shaft driven by a drive shaft, rotatably supported during The end wall of the rotor has a slight play against the lateral boundary wall of the casing notch. It rotates along the boundary wall surface, extends in the radial direction, and extends in the longitudinal direction. having vanes guided in slits in the rotor that are consistent in the direction of the case; At least one structure formed between the inner wall surface of the shing notch and the circumferential surface of the rotor. The chamber is divided into a low pressure chamber and a high pressure chamber, and the low pressure chamber expands through an inflow opening. The high-pressure chamber communicates with the supply passage leading to the coolant, and the high-pressure chamber is connected via an outflow opening with an outflow valve. In a vane type compressor that communicates with the pressure passage, each low pressure chamber (30, 31) so that the cooling medium flows axially from opposite directions. Inlet openings (34 and 34) on mutually facing end sides of the pressure chambers (30, 31) 36) are provided on both side boundary walls (15, 16), and the same connected to the inflow openings (34 or 35, 36) provided on the boundary walls (15, 16); Advantageously, the feed passages (38, 39, 40) passing through the rotor have approximately the same length. A common supply chamber (41, 4) symmetrical about the axis (20) and filled with cooling medium 2), and each supply chamber (41, 42) has a boundary wall (15, 16). ), provided on the opposite side of the rotor (18) and coaxially with the rotor shaft (20). A vane compressor characterized by: 2 The supply passages (38, 39, 40) are approximately radial from the individual supply chambers (41, 42) 2. The vane compressor according to claim 1, wherein the vane compressor is bifurcated in a direction. 3. The free end of the rotor shaft (20) on the opposite side to the drive shaft (25) a first supply chamber (42) connectable to a return conduit (43) of the cooling medium in the direction The second supply chamber (41) surrounds the rotor shaft (20) as an annular chamber. The rotor shaft (20) is open at the free end of the rotor shaft (20) and rotates. an annular feeding chamber through at least one radial hole (45) in the child shaft (20); Claim 1 or 2, characterized in that it has a blind hole (44) communicating with (41). The vane compressor described. 4 Effectively utilizes the weir pressure generated when the cooling medium flows into the supply passages (39, 40) A small amount of cooling medium is supplied directly from the first supply chamber (42) to the vane guide shaft. Limited by the vane bottom (58) in the slit (27) and the slit bottom (57) The vane (28) is guided into the hollow chamber (56) formed by the vane guide slit (2). 7) When pushed inside, the small amount of cooling medium is guided to the end face of the rotor. from which it flows into at least one working room (21, 22). The vane compressor according to claim 3, characterized in that: 5 The border of the casing notch (14) located immediately next to the first supply chamber (42) having arc-shaped recesses (59, 60) on the boundary wall surface and penetrating the boundary wall surface (16); Advantageously, the recesses (59, 60) are provided via axially provided holes (63, 64). communicates with the first supply chamber (42), and the vane (28) communicates with the low pressure chamber (30, 3). 1), the vane bottom surface (58) and the slit in the vane guide slit (27) It passes through a hollow chamber (56) partitioned by a bottom surface (57) of the lit. The vane compressor according to claim 4, characterized in that: 6 Arc-shaped grooves (65, 66) are provided on both boundary walls of the casing notch (14). When the vane (28) passes through the high pressure chamber (32, 33), the groove (65, 66) is the vane bottom surface (58) in the vane guide slit (27) and the slit bottom surface. (57) and communicates with the hollow chamber (56) separated by The vane compressor according to claim 4 or 5, characterized in that: 7 Recesses (59, 60) or grooves (65, 66) having a slight width in the radial direction , with its central longitudinal edge (61 or 62), the vane guide slit (27) is located almost on the rotating orbit extending from the slit bottom (57), and in the circumferential direction. and at least one of the low pressure chambers (30, 31) or the high pressure chambers (32, 33) Claim 5 or 6, characterized in that it extends over a partial region of vane type compressor.