High pressure ratio gas turbine engine

Abstract

A gas turbine engine including: a high pressure turbine, a low pressure turbine, a high pressure compressor coupled to the high pressure turbine by a high pressure shaft, a propulsor and a low pressure compressor coupled to the low pressure turbine via a low pressure shaft and a reduction gearbox; wherein the high pressure compressor defines an average stage pressure ratio at cruise conditions of between 1.25 and 1.35 and consists of 10 or 11 stages; and the high pressure compressor and low pressure compressor together define a core overall pressure ratio at cruise conditions of between 40:1 and 60:1.

Claims

1. A gas turbine engine comprising: a high-pressure turbine; a low-pressure turbine; a high-pressure compressor coupled to the high-pressure turbine by a high-pressure shaft; and a propulsor and a low-pressure compressor coupled to the low-pressure turbine via a low-pressure shaft and a reduction gearbox, wherein the high-pressure compressor defines an average stage pressure ratio at cruise conditions of between 1.25 and 1.35 and consists of 10 or 11 stages, the high-pressure compressor and low-pressure compressor together define a core overall pressure ratio at cruise conditions of between 40:1 and 60:1, the low-pressure compressor consists of between 3 or 4 stages, the low-pressure compressor defines a cruise pressure ratio of between approximately 1.5 and 3.5, and wherein, when the high-pressure compressor comprises 10 stages, the average stage pressure ratio at cruise conditions is between 1.25 and 1.35 at a cruise pressure ratio of between 10:1 and 20:1, and when the high-pressure compressor comprises 11 stages, the average stage pressure ratio at cruise conditions is between 1.25 and 1.35 at a cruise pressure ratio of between 12:1 and 27:1.

2. A gas turbine engine according to claim 1, wherein the high and low pressure compressors are configured to define a relative rotor inlet Mach number of between 1.0 and 1.2 at cruise conditions.

3. A gas turbine engine according to claim 1, wherein the high pressure compressor defines an inlet rotor hub to tip ratio of between 0.45 and 0.6.

4. A gas turbine engine according to claim 1, wherein the low and high pressure compressor define a core overall pressure ratio at cruise conditions between 36:1 and 56:1.

5. A gas turbine engine according to claim 1, wherein the high pressure turbine consists of two or fewer stages.

6. A gas turbine engine according to claim 1, wherein the low pressure turbine consists of five or fewer stages.

7. A method of operating the gas turbine engine of claim 1, comprising, at cruise conditions, operating the high pressure compressor to provide an average stage pressure ratio of between 1.25 and 1.35, and operating the low pressure and high pressure compressors to provide a core overall pressure ratio of between 40:1 and 60:1.

8. A gas turbine engine according to claim 3, wherein the high pressure compressor defines an inlet rotor hub to tip ratio of approximately 0.5.

Description

(1) Embodiments will now be described by way of example only, with reference to the Figures, in which:

(2) FIG. 1 is a sectional side view of a gas turbine engine;

(3) FIG. 2 is a close up sectional side view of an upstream portion of the gas turbine engine of FIG. 1;

(4) FIG. 3 is a close up sectional side view of a turbine section of the gas turbine engine of FIG. 1;

(5) FIG. 4 is a sectional front view of a reduction gearbox of the gas turbine engine of FIG. 1;

(6) FIG. 5 is a graph illustrating a design space for the compressor section of FIG. 2;

(7) FIG. 6 is a graph illustrating a design space for a high pressure compressor of the compressor section of FIG. 2;

(8) FIG. 7 is a graph illustrating a design space for a low pressure compressor of the compressor section of FIG. 2; and

(9) FIG. 8 is a diagram illustrating airflows relative to a compressor blade of the compressor section of FIG. 2.

(10) FIG. 1 illustrates a gas turbine engine 10 having a principal rotational axis 9. The engine 10 comprises an air intake 12 and a propulsive fan 23 that generates two airflows: a core airflow A and a bypass airflow B. The gas turbine engine 10 comprises a core 11 that receives the core airflow A. The engine core 11 comprises, in axial flow series, a low pressure compressor 14, a high-pressure compressor 15, combustion equipment 16, a high-pressure turbine 17, a low pressure turbine 19 and a core exhaust nozzle 20. A nacelle 21 surrounds the gas turbine engine 10 and defines a bypass duct 22 and a bypass exhaust nozzle 18. The bypass airflow B flows through the bypass duct 22. The fan 23 is attached to and driven by the low pressure turbine 19 via a shaft 26 and an epicyclic gearbox 30.

(11) In use, the core airflow A is accelerated and compressed by the low pressure compressor 14 and directed into the high pressure compressor 15 where further compression takes place. The compressed air exhausted from the high pressure compressor 15 is directed into the combustion equipment 16 where it is mixed with fuel and the mixture is combusted. The resultant hot combustion products then expand through, and thereby drive, the high pressure and low pressure turbines 17, 19 before being exhausted through the nozzle 20 to provide some propulsive thrust. The high pressure turbine 17 drives the high pressure compressor 15 by a suitable interconnecting shaft 27. The fan 23 generally provides the majority of the propulsive thrust. The epicyclic gearbox 30 is a reduction gearbox.

(12) An exemplary arrangement for a geared fan gas turbine engine 10 is shown in FIG. 4. The low pressure turbine 19 (see FIG. 1) drives the shaft 26, which is coupled to a sun wheel, or sun gear, 28 of the epicyclic gear arrangement 30. Radially outwardly of the sun gear 28 and intermeshing therewith is a plurality of planet gears 32 that are coupled together by a planet carrier 34. The planet carrier 34 constrains the planet gears 32 to precess around the sun gear 28 in synchronicity whilst enabling each planet gear 32 to rotate about its own axis. The planet carrier 34 is coupled via linkages 36 to the fan 23 in order to drive its rotation about the engine axis 9. Radially outwardly of the planet gears 32 and intermeshing therewith is an annulus or ring gear 38 that is coupled, via linkages 40, to a stationary supporting structure 24.

(13) Note that the terms “low pressure turbine” and “low pressure compressor” as used herein may be taken to mean the lowest pressure turbine stages and lowest pressure compressor stages (i.e. not including the fan 23) respectively and/or the turbine and compressor stages that are connected together by the interconnecting shaft 26 with the lowest rotational speed in the engine (i.e. not including the gearbox output shaft that drives the fan 23). In some literature, the “low pressure turbine” and “low pressure compressor” referred to herein may alternatively be known as the “intermediate pressure turbine” and “intermediate pressure compressor”. Where such alternative nomenclature is used, the fan 23 may be referred to as a first, or lowest pressure, compression stage.

(14) The epicyclic gearbox 30 is shown by way of example in greater detail in FIG. 4. Each of the sun gear 28, planet gears 32 and ring gear 38 comprise teeth about their periphery to intermesh with the other gears. However, for clarity only exemplary portions of the teeth are illustrated in FIG. 4. There are four planet gears 32 illustrated, although it will be apparent to the skilled reader that more or fewer planet gears 32 may be provided within the scope of the claimed invention. Practical applications of a planetary epicyclic gearbox 30 generally comprise at least three planet gears 32.

(15) The epicyclic gearbox 30 illustrated by way of example in FIG. 4 is of the planetary type, in that the planet carrier 34 is coupled to an output shaft via linkages 36, with the ring gear 38 fixed. However, any other suitable type of epicyclic gearbox 30 may be used. By way of further example, the epicyclic gearbox 30 may be a star arrangement, in which the planet carrier 34 is held fixed, with the ring (or annulus) gear 38 allowed to rotate. In such an arrangement the fan 23 is driven by the ring gear 38. By way of further alternative example, the gearbox 30 may be a differential gearbox in which the ring gear 38 and the planet carrier 34 are both allowed to rotate.

(16) It will be appreciated that the arrangement shown in FIG. 4 is by way of example only, and various alternatives are within the scope of the present disclosure. Purely by way of example, any suitable arrangement may be used for locating the gearbox 30 in the engine 10 and/or for connecting the gearbox 30 to the engine 10. By way of further example, the connections (such as the linkages 36, 40 in the FIG. 1 example) between the gearbox 30 and other parts of the engine 10 (such as the input shaft 26, the output shaft and the fixed structure 24) may have any desired degree of stiffness or flexibility. By way of further example, any suitable arrangement of the bearings between rotating and stationary parts of the engine (for example between the input and output shafts from the gearbox and the fixed structures, such as the gearbox casing) may be used, and the disclosure is not limited to the exemplary arrangement of FIG. 2. For example, where the gearbox 30 has a star arrangement (described above), the skilled person would readily understand that the arrangement of output and support linkages and bearing locations would typically be different to that shown by way of example in FIG. 2.

(17) Accordingly, the present disclosure extends to a gas turbine engine having any arrangement of gearbox styles (for example star or planetary), support structures, input and output shaft arrangement, and bearing locations.

(18) Other gas turbine engines to which the present disclosure may be applied may have alternative configurations. By way of further example, the gas turbine engine shown in FIG. 1 has a split flow nozzle 18, 20 meaning that the flow through the bypass duct 22 has its own nozzle 18 that is separate to and radially outside the core engine nozzle 20. However, this is not limiting, and any aspect of the present disclosure may also apply to engines in which the flow through the bypass duct 22 and the flow through the core 11 are mixed, or combined, before (or upstream of) a single nozzle, which may be referred to as a mixed flow nozzle. One or both nozzles (whether mixed or split flow) may have a fixed or variable area. Whilst the described example relates to a turbofan engine, the disclosure may apply, for example, to any type of gas turbine engine, such as an open rotor (in which the fan stage is not surrounded by a nacelle) or turboprop engine, for example.

(19) The geometry of the gas turbine engine 10, and components thereof, is defined by a conventional axis system, comprising an axial direction (which is aligned with the rotational axis 9), a radial direction (in the bottom-to-top direction in FIG. 1), and a circumferential direction (perpendicular to the page in the FIG. 1 view). The axial, radial and circumferential directions are mutually perpendicular.

(20) Referring now to FIG. 2, the low pressure and high pressure compressor 14, 15 are shown in more detail. As can be seen, each of the compressors comprises a multi-stage, axial flow compressor.

(21) The low pressure compressor consists of between three and five stages inclusive (i.e. no more than five stages, and no fewer than three stages) 41a-d. Each stage 41a-d comprises at least one respective compressor rotor 43, and may comprise a respective stator 44. The respective rotor 43 and stator 44 are generally axially spaced. In the present case, the first stator 44 is downstream in core flow of the first rotor 43. One or more further stators such as an inlet stator (not shown) may be provided—however, since no additional rotor is associated with the inlet stator, this does not constitute an additional stage, since no pressure rise is provided by the inlet stator alone. As will be appreciated by the person skilled in the art, the rotors 43 are coupled to the respective shaft (i.e. the low pressure shaft 26 in the case of the low pressure compressor 14) by corresponding discs 46a-d, and so turn with the shaft 26. On the other hand, the stators 44 are held stationary. In some cases, the stators 44 may pivot about their long axes, to adjust the angle of attack and inlet and outlet area for the respective compressor stage. Such stators are known as “variable stator vanes” or VSVs.

(22) The high pressure compressor 15 similarly consists of ten or eleven stages, and in the described embodiment consists of ten stages 42a-j. Again, each stage comprises at least a rotor, and may also comprise a stator.

(23) The turbine is shown in FIG. 3. To drive the high pressure compressor 15, a high pressure turbine 17 having two stages 47a, 47b may be necessary. Again, the number of turbine stages can be determined in a similar manner to the number of compressor stages. Alternatively, a single turbine stage may be provided. In particular, it has been found that high pressure compressors having cruise pressure ratios up to 13:1 can be driven by single stage turbines. Similarly, to drive the low pressure compressor 14 and fan 23, three or four low pressure turbine stages 49a-c are provided. In some cases, five compressor stages may be provided.

(24) Between them, the high and low pressure compressors 15, 16 define a maximum in use overall core pressure ratio (OPR). The core OPR is defined as the ratio of the stagnation pressure upstream of the first stage 44 of the low pressure compressor 15 to the stagnation pressure at the exit of the highest pressure compressor 16 (before entry into the combustor). The core OPR excludes any pressure rise generated by the fan 23 where the fan provides air flow to the core, so a total engine overall pressure ratio (EPR) may be higher than the core OPR. In the present disclosure, the overall core OPR is between 40:1 and 60:1 inclusive. In the described embodiment, the core OPR is 50, and may take any value between these upper and lower bounds. For example, the core OPR may be any of 40, 45, 50, 55 and 60, or any value between these values.

(25) As will be understood, the core OPR will vary according to atmospheric, flight and engine conditions. However, the cruise OPR is as defined above.

(26) As will be understood, a large design space must be considered when designing a gas turbine engine to determine an optimal engine with respect to a chosen metric (such as engine weight, cost, thermal efficiency, propulsive efficiency, or a balance of these). In many cases, there may be a large number of feasible solutions for a given set of conditions to achieve a desired metric.

(27) One such variable is core OPR. As core OPR increases, thermal efficiency also tends to increase, and so a high OPR is desirable. Even once a particular OPR is chosen however, a number of design variables must be chosen to meet the chosen OPR.

(28) One such design variable is the amount of pressure rise provided by the low pressure compressor 15 relative to that provided by the high pressure compressor 16 (sometimes referred to as “worksplit”). As will be understood, the total core OPR can be determined by multiplying the low pressure compressor pressure ratio (i.e. the ratio between the stagnation pressure at the outlet of the low pressure compressor to the stagnation pressure at the inlet of the low pressure compressor 15) by the high pressure compressor ratio (i.e. the ratio between the stagnation pressure at the outlet of the high pressure compressor 16 to the stagnation pressure at the inlet of the high pressure compressor 16). Consequently, a higher core OPR can be provided by increasing the high pressure compressor ratio, the low pressure compressor ratio, or both.

(29) It will be understood that the stage loading can be managed by one or more of changing the rotor speed at the cruise compression conditions, changing the turning provided by the blades, or changing the radius of the tips of the compressor rotors, which in turn necessitates an increase in the radius of the roots of the compressor rotors to maintain a given flow area. Each of these options has associated advantages and disadvantages. For instance, increasing high pressure compressor rotor speed or radius in combination with a high work low pressure compressor results in higher centrifugal loads and larger discs and blades respectively, both of which result in higher weight. Furthermore, increasing the rotor blade tip speed (by either increasing rotational speed or radius) results in higher rotor blade relative Mach number. Beyond a certain point, this may lead to a lower efficiency, since the increased rotor tip speed or higher turning leads to lower compressor efficiencies, in view of losses associated with aerodynamic shocks as the tips significantly exceed the speed of sound.

(30) FIG. 8 shows how the relative tip Mach number can be calculated. Each compressor rotor blade 43 rotates about the engine axis 9, in a circumferential direction, shown by the large arrow in FIG. 8. This circumferential movement defines a blade tip speed V.sub.w1. The rotor also causes “whirl” of air in the circumferential direction V.sub.w0. This whirl can be subtracted from the blade physical tip speed to give a blade speed velocity vector U.sub.1 of incoming airflow from the reference frame of the blade. The air incoming to the compressor also has an axial velocity component V.sub.m1 from the reference frame of the blade, due to forward aircraft movement, and due to compression by upstream stages. The rotor relative inlet velocity V.sub.1 is then the vector sum of the blade speed velocity vector U.sub.1 and inlet velocity V.sub.m1. For a given velocity V.sub.1 and local speed of sound, a relative Mach number can be calculated as follows:

(31) $\mathrm{Relative}\mathrm{Mach}\mathrm{number}=\frac{\mathrm{velocity}}{\mathrm{Speed}\mathrm{of}\mathrm{sound}}$

(32) A second option is to increase the number of stages in the respective compressors, thereby maintaining a low stage loading, low rotational speed, and low disc weight. Again, this can be achieved by adding a stage to either the low pressure compressor 15 or high pressure compressor 16. However, this will generally result in a higher weight and cost associated with the additional stage.

(33) A further complication is the presence of the gearbox 30. The gearbox provides additional design freedom, since, as noted above, the gearbox reduction ratio can be selected to provide a preferred fan tip speed independently of both fan radius and low pressure compressor rotor speed. However, the gearbox also presents constraints in view of its large size. Consequently, the large radius required radially inward of the fan 23 inherent in a geared turbofan having an epicyclic gearbox dictates a fan 23 having a large hub radius, i.e. a large radial distance between the engine centre 9 and the aerodynamic root of the fan blades 23. Furthermore, in view of the relatively slow turning fan typical of geared turbofans, relatively little pressure rise is provided by the inner radius of the fan 23, and so geared turbofans tend to have a high hub to tip ratio fan 23.

(34) The inventors have explored this design space, and found an optimum range of stage numbers and compressor pressure ratios, that provides an optimal mix of weight and efficiency.

(35) The inventors have found that a particularly efficient work split for a gas turbine engine having a core OPR in the above described range can be provided by providing a high pressure compressor 15 which provides a relatively high pressure ratio (between 12:1 and 27:1). This is feasible, since the high pressure compressor typically features one or more rows of variable stator vanes, and has a relatively small variability in shaft speed during use (e.g. maximum shaft speed at maximum take-off conditions is typically only around double the minimum shaft speed at idle). On the other hand, providing such a high pressure ratio utilising relatively few rotor blades (i.e. with a high average stage loading) has been found to result in low compressor efficiency, particularly where significant work is provided by the low pressure compressor, which may provide high speed, high temperature inlet air. Consequently, in the present disclosure, a high pressure compressor is used having either ten or eleven stages, and an average stage loading of between 1.25 and 1.35. Stage loading is defined as the stagnation pressure ratio across an individual stage (rotor and stator) of a compressor. Similarly, an average stage loading can be defined as the sum of the stage loadings of each compressor stage of a compressor, divided by the number of stages. Such a design has been found to result in a high efficiency high pressure compressor, that, in combination with the low pressure compressor 14, can provide the desired high overall pressure ratio, without sacrificing compressor efficiency.

(36) The inventors have found that it is advantageous to combine the above described high pressure compressor 15 with a low pressure compressor 14 consisting of three or four stages, and having a cruise pressure ratio of between 1.5:1 and 3.5:1.

(37) The above combination of compressor parameters has been found to provide an inlet relative Mach number to the high pressure compressor first rotor stage 42a of less than 1.2, and preferably between 1.0 and 1.2. Such a range of Mach numbers ensures that shock losses are kept low, ensuring high compressor efficiency.

(38) An example compression system comprising a low pressure compressor 14 and high pressure compressor 15 is described, which provides for a cruise inlet relative Mach number of less than 1.2.

(39) The high pressure compressor comprises a hub to tip ratio (i.e. a ratio of the radius R.sub.1 of a radially inner blade root of the first rotor blade of the first high pressure compressor stage 42a, to a radius R.sub.2 of a radially outer blade tip of the first rotor blade) of between 0.45 and 0.6, and in this embodiment, the hub to tip ratio is 0.5. Such a geometry is thought to provide good efficiency, in combination with part speed stability.

(40) The high pressure compressor 15 is configured to have a rotational speed at cruise conditions of approximately xxxx revolutions per minuted (RPM). A high pressure compressor 15 axial inlet Mach number, which is provided by air flowing from the upstream low pressure compressor 14 is between Mach xxx and yyy. As will be appreciated, the Mach number will be a consequence of the axial velocity and temperature of air at the high pressure compressor 15 inlet. The radius of the high pressure compressor blade tip is xxxx, and so a relatively tip Mach number of xxx is provided.

(41) Referring to FIG. 5, the above optimum parameters define a design space for the compressors 14, 15 (shown as the hatched region on the graph).

(42) It is a requirement of the disclosed engine to provide an overall core pressure ratio of between 40:1 and 60:1. Lines OPR.sub.40, OP.sub.60 illustrate the allowable low pressure and high pressure compressor pressure ratios necessary to achieve this requirement.

(43) Similarly, FIG. 6 shows high pressure compressor stage numbers required for corresponding high pressure compressor 15 cruise pressure ratios and average pressure ratios per stage. The hatched area shows the design space defined by the present disclosure.

(44) FIG. 7 shows low pressure compressor stage numbers required for corresponding low pressure compressor 14 cruise pressure ratios and average pressure ratios per stage. The hatched area shows the design space defined by the present disclosure.

(45) The designer is hence taught how to design a compressor system which achieves the desired characteristics of high overall core cruise pressure ratio (between 40:1 and 60:1), while minimising stage count and maximising compressor efficiency.

(46) An example gas turbine engines that has been considered by the inventors is described below.

(47) A first example engine has a maximum take-off thrust at sea level under ISO conditions of approximately xxxx pounds-force (lbf). The low pressure compressor has four stages, and is configured to provide a cruise pressure ratio of approximately x. The high pressure compressor is configured to provide a cruise pressure ratio of approximately y. This gives an overall core pressure ratio of approximately z. Such an engine is thought to provide an optimum mix of weight and thermal efficiency for an engine in this class, since weight is a more important factor in this class than for higher thrust engines, in view of the shorter typical mission ranges of aircraft for which engines of this thrust are designed.

(48) It will be understood that the invention is not limited to the embodiments above-described and various modifications and improvements can be made without departing from the concepts described herein. Except where mutually exclusive, any of the features may be employed separately or in combination with any other features and the disclosure extends to and includes all combinations and sub-combinations of one or more features described herein.