Axial flow turbo compressor
An axial flow compressor including one or more axially spaced stator sections (14) each having a circumferential array of guide vanes (15), and one or more rotor section (12, 16) each having a circumferential array of rotor blades (13, 17; A, B), and between successive rotor blades (A, B) there are formed flow paths and between the stator and rotor sections there are provided axial gaps (22, 23, 24) of a diverging configuration so as to form in each flow path a diffusion region (C) which extends from a narrowest cross section (a2) of the flow path located at a certain distance upstream of the leading edge of a second rotor blade (B) to a wider cross section (a3) located approximately at the leading edge of the second rotor blade (B), wherein each flow path has a transition region (D) of a substantially non-increasing cross sectional area extending from the wider cross section (a3) to the trailing edges of the rotor blades (A, B).
The invention relates to a turbo compressor of the axial flow type comprising a stator with at least one axial section including a circumferential array of flow directing guide vanes and a rotor with at least one axial section including a circumferential array of rotor blades, wherein between the guide vanes and the rotor blades and between an inner peripheral wall and an outer peripheral wall there are formed parallel flow paths, and between successive rotor blades there are formed rotor flow passages through which the flow paths extend.
In prior art compressors of the above type there is a problem of obtaining an increased pressure ratio across each compressor stage and/or an increased efficiency. A factor which is limiting and crucial for these objectives is the mean velocity of the air flow through the compressor. It is a well known fact that an increased air flow velocity would give a higher pressure ratio across each compressor stage and/or an increased efficiency. In prior art compressors, however, the flow velocity is kept well below the sonic velocity, i.e. a Mach number below 1.0, usually around 0.7, because at super sonic velocity there arise shock waves in the air flow which are difficult to avoid and which are detrimental to the pressure ratio and the compressor efficiency. By keeping the Mach number around 0.7 there is ensured that the Mach number 1.0 will not be reached and that no shock waves will arise.
The reason for using such a large “safety” margin of 0.7-1.0 in Mach number is that in prior art compressors the air flow velocity normally increases locally at the downstream ends of the flow paths of the stator or rotor sections. The reason for such velocity increase is that when departing from a flow path between two guide vanes or two drive blades the air flow is subjected to a tangential contraction due to a change in flow direction. Such an increase of the flow velocity might bring the air flow velocity up to a Mach number around 1.0, and undesired shock waves might arise in the air flow. In order to make sure that sonic velocity is not reached at any location in the compressor, the air flow velocity is kept down to the “safe” Mach number 0.7.
There are transonic compressors working at velocities exceeding Mach number 1.0 and by which special arrangements have been made to avoid the negative influence of shock waves. However, that type of compressor would also benefit from lower air flow losses in the stator and rotor flow paths in accordance with the invention.
The main object of the invention is to accomplish a compressor of the above type working at subsonic air flow velocities and where the air flow passages through the compressor are improved in such a way that the mean air flow velocity through the stator and rotor sections may be increased considerably without risking the Mach number reaching the 1.0 level.
Further objects and advantages of the invention will appear from the following specification and claims.
A preferred embodiment of the invention is hereinafter described in detail with reference to the accompanying drawing.
On the drawing
In
When reaching a section a2 at a certain distance upstream of the leading edge of the second rotor blade B or slightly downstream of the leading edge of the first rotor blade A the flow path passes through a diffusor region C which extends in the flow direction to a section a3 approximately at the leading edge of the second rotor blade B. Accordingly, the diffusor region C has an entrance section a2 and an exit section a3, wherein the entrance section a2 has a cross sectional area which is smaller than that of the exit section a3. The entrance section a2 of the diffusor region C is also the narrowest cross section of the entire flow path between a1 and a4.
Downstream of the diffusor region C, the flow path extends through a transition region D which has a substantially non-increasing or slightly decreasing cross sectional area all the way from section a3 to an exit section a4. To compensate for a downstream increasing distance between the rotor blades A and B the radial extent of the rotor blades, i.e. the radial distance between the inner peripheral wall 28 and the outer peripheral wall 29, has to be reduced so as to keep the cross sectional area substantially constant throughout the transition region D. See
Upstream of the diffusor region C, the flow path has a substantially constant cross sectional area, from an initial section a1 to the diffusor region entrance section a2 so as to generate a non-increasing flow velocity. As illustrated in
By locating the diffusor region C of each flow path upstream of the flow deflecting transition region D between two successive rotor blades A, B there is accomplished a reduction in flow velocity and, hence, a reduction of the flow losses during the flow path deflection between the rotor blades A, B. This means an improved efficiency of the compressor.
In order to ensure a good efficiency of the compressor the flow velocity shall be equally high over the entire radial extent of each rotor blade. This is accomplished by employing a guide vane configuration in the initial compressor stage such that each guide vane 10 has a different flow deflection angle at its top end compared to its bottom end. See
In
In
Between the stator sections and the rotor sections there are provided axial gaps which form annular air flow passages 22, 23 and 24.
The main character of the air flow passage through the compressor is successively converging from the inlet nozzle end toward the outlet end. As illustrated in
A characteristic feature of the invention is the provision of the axial gaps between the stator and rotor sections forming the flow passages 22, 23 and 24. The reason for introducing these axially extended and radially diverging passages 22, 23 and 24 is to accomplish a velocity reducing diffusor region with the purpose to reduce flow losses and increase the compressor efficiency.
As illustrated in
This undesirable acceleration of the air flow is omitted by increasing the available cross sectional area in the flow passage, i.e. by the introduction of the intermediate and radially diverging flow passages 22, 23 and 24. By increasing the radial extent of these passages by at least 10% there is obtained an improved compressor efficiency. For obtaining a substantial increase in the compressor efficiency the increase in the radial extent of the flow passages 22, 23 and 24 should be at least 20%. In the illustrated example, the radial extent of the passages increases from h1 at the entrance to h2 at the exit end.
For obtaining a favourable shape of the air flow path through the compressor, the increase in radial extent of the intermediate passages 22, 23 and 24 has to be accomplished over a certain passage length. Therefore, the passages 22, 23 and 24 should have an axial length exceeding 30% of the rotor blade and guide vane length, respectively. Depending on the radial extent of the blades and vanes the passage length could be 50% or more of the length of the blades and vanes, respectively.
Claims
1. Axial flow turbine compressor, comprising a stator with at least one axial section including a circumferential array of flow directing guide vanes (13,17), a rotor with at least one axial section including a circumferential array of rotor blades (15; A, B), an inner peripheral wall (28), and an outer peripheral wall (29), wherein a flow path is formed between every two successive rotor blades (A,B) in the direction of rotor rotation (ω) and between said inner and outer peripheral walls (28,29), characterized in that each flow path comprises
- a narrowest cross sectional area at a first cross section (a2) located at a certain distance upstream of the leading edge of a second rotor blade (B) in the direction of rotor rotation (ω),
- a diffusion region (C) having a successively increasing cross sectional area in the flow direction and extending from said first cross section (a2) to a second cross section (a3) located approximately at the leading edge of said second rotor blade (B), and
- a transition region (D) extending in the flow direction from said second cross section (a3) to the trailing edge of said second rotor blade (B), said transition region (D) has a substantially non-increasing cross sectional area in the flow direction throughout its length.
2. Turbine compressor according to claim 1, wherein the transverse distance between said first and second rotor blades (A,B) increases throughout said transition region (D), whereas the radial distance between said inner peripheral wall (28) and said outer peripheral wall (29) decreases such that the cross sectional area of the flow path does not increase throughout said transition region (D).
3. Turbine compressor according to claim 1 or 2, wherein the flow through said diffusion region (C) is substantially laminar.
4. Turbine compressor according to anyone of claims 1-3, wherein each flow path upstream of said diffusion region (C) has a substantially constant cross sectional area.
5. Axial flow type turbine compressor, comprising a stator with at least one circumferential row of flow directing guide vanes. (13,17), and a rotor with at least one circumferential row of rotor blades (15; A,B), wherein between said guide vanes (13,17) and said rotor blades (15; A,B) there are formed a number of parallel flow paths, and between successive rotor blades (A,B) there are formed rotor flow passages through which said flow paths extend, characterized in that each flow path has a diffusion region (C) extending from a location approximately at the leading edge of a first one (A) of said successive rotor blades (A,B) to a location approximately at the leading edge of a second rotor blade (B) in the rotation direction (ω) of said rotor, wherein each one of said rotor flow passages downstream of said diffusion region (C) has a substantially non-increasing cross sectional area throughout its length.
6. Turbine compressor according to claim 5, wherein said flow paths as well as said rotor flow passages are partly defined by an outer peripheral wall (29) and an inner peripheral wall (28).
7. Turbine compressor according to claim 5 or 6, wherein each one of said rotor flow passages is defined by a first rotor blade (A), and a second rotor blade (B) succeeding said first rotor blade (A) in the direction of rotor rotation (ω), said diffusion region (D) extends in the flow direction from a location approximately at the leading edge of said first rotor blade (A) to a location approximately at the leading edge of said second rotor blade (B), and each one of said flow paths has a narrowest cross sectional area (a2) at the upstream end of said diffusion region (C).
8. Turbine compressor according to claim 1, wherein said guide vanes (13,17) are arranged in two or more axially spaced stator sections, and said rotor blades (15) are arranged in two or more axially spaced rotor sections,
- said rotor sections and said stator sections are arranged with an axial gap (22,23,24) between them,
- said axial gap (22,23,24) having an axial width of at least 30% of the chord length of the preceding guide vane (13,17) or rotor blade (15), and
- said axial gap (22,23,24) forms a flow passage region with a,radially diverging shape in the axial direction.
9. Turbine compressor according to claim 8, wherein said flow passage region has a radial extent (h2) at its downstream end that is at least 10% larger than the radial extent (h1) at its upstream end.
10. Turbine compressor according to claim 8, wherein said flow passage region has an axial width of at least 50% of the chord length of the preceding guide vane (13,17) or rotor blade (15).
Type: Application
Filed: Nov 2, 2001
Publication Date: Aug 11, 2005
Inventor: Rolf Jacobsson (Saltsjoboo)
Application Number: 10/415,801