Comparison of efficiency losses due to leaks for turbine units of aviation air conditioning systems with petal-type gas-dynamic bearings and ball bearings

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Abstract

BACKGROUND: Designers of turbomachines strive to increase the efficiency of expanding compressed gases by reducing all kinds of energy losses, particularly due to clearances between the impeller and the body elements of the turbomachine.

AIM: This article aimed to evaluate a possible increase in efficiency with a decrease in the radial and axial clearance between the blades of a radial-axial impeller and the casing of a centrifugal expander in the designs of turbomachines with ball bearings and petal-type gas-dynamic bearings.

MATERIALS AND METHODS: The radial and axial clearances between the blades of the radial-axial impeller and the centrifugal expander casing in the designs of turbomachines with ball bearings and petal-type gas-dynamic bearings were compared by analyzing the experience of Russian and international experts in developing turbomachines. Models were presented for estimating the efficiency losses of a centrifugal expander depending on the value of the radial and axial clearances. A comparative calculation of the efficiency loss for medium- and high-cooling-capacity refrigeration turbines of aircraft air conditioning systems was performed.

RESULTS: Based on the calculations, a conclusion was derived about the predominance of the influence of the radial clearance. The calculations revealed that with a decrease in the clearances between the impeller and the casing in a design with petal-type bearings, a refrigeration turbine of medium cooling capacity (16 kW, 2 impellers) can be expected to experience an increase in efficiency by an average of 2.3%; this expected increase is 0.75% to 1.4% for a high-capacity refrigeration turbine (55 kW, 3 or 4 impellers). Findings indicate that performing works to reduce radial clearances in the designs of turbomachines with petal-type gas-dynamic bearings is necessary.

About the authors

Vitaly S. Nikolaev

Bauman Moscow State Technical University; PJSC NPO Nauka

Author for correspondence.
Email: vs.nikolaev.bmstu@gmail.com
SPIN-code: 5847-3632

Postgraduate Student

Russian Federation, 5, 2-nd Baumanskaya, Moscow, 105005; Moscow

Sergey A. Abalakin

PJSC NPO Nauka

Email: SA.Abalakin@gmail.com

Design Engineer

Russian Federation, Moscow

Igor V. Tishchenko

Bauman Moscow State Technical University; PJSC NPO Nauka

Email: iv.tischenko@bmstu.ru
SPIN-code: 5630-4301
Scopus Author ID: 632877

Ph.D. (Engin.), Associate Professor

Russian Federation, 5, 2-nd Baumanskaya, Moscow, 105005; Moscow

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Supplementary files

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2. Fig. 1. Scheme of gas flow in the flow path of a radial-axial turbine: d1 – outer diameter of the impeller, d2 – average diameter of the impeller at the outlet, d0 – diameter of the impeller funnel, dвт – diameter of the impeller hub, l1 and l2 – blade height at the impeller inlet and outlet, respectively, Δx – axial clearance, Δr – radial clearance.

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3. Fig. 2. Sources of clearances in a ball bearing (a) and a petal-type gas-dynamic bearing (b): Δ – radial clearance; C – mounting clearance, h – height of the corrugations of the elastic damper.

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4. Fig. 3. Graphs of estimates of efficiency loss as a function of the radial clearance in the centrifugal expander of medium cooling capacity (16 kW) of the refrigeration turbine on petal-type gas-dynamic bearings, =0,864 (the formula sources are given in Table).

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5. Fig. 4. Graphs of estimates of efficiency loss as a function of the radial clearance in the centrifugal expander with a large cooling capacity (55 kW) of a refrigeration turbine on petal-type gas-dynamic bearings, =0,850 (designations are given in Fig. 3).

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6. Fig. 5. Graphs of estimates of efficiency loss as a function of the value of the radial clearance in a large refrigeration turbine on petal-type gas-dynamic bearings with two stages of expansion. A – stage 1 (cooling capacity 23 kW), ; B – stage 2 (cooling capacity 24.7 kW),  (designations are given in Fig. 3).

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Copyright (c) 2022 Nikolaev V.S., Abalakin S.A., Tishchenko I.V.

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