WO2017131560A2

WO2017131560A2 - Buffer device

Info

Publication number: WO2017131560A2
Application number: PCT/RU2017/000121
Authority: WO
Inventors: Евгений Павлович ПОЗДНЯКОВ
Original assignee: Евгений Павлович ПОЗДНЯКОВ
Priority date: 2016-01-26
Filing date: 2017-03-09
Publication date: 2017-08-03
Also published as: WO2017131560A3; RU2016102366A; RU2016102366A3

Abstract

The invention relates to heat engines and may be applied in various types of gas turbine engines and air-jet engines having a single-phase working body for feeding a working body into a heater. The invention allows for avoiding the use of circulating fans otherwise necessary for the operation of a buffer device. A rotor of a buffer device is made in the form of blades, and a working body is circulated in the buffer device via the motive force of said blades.

Description

BUFFER

The invention relates to heat engines and can be used in gas turbine and jet engines of various types with a single-phase working fluid.

5 A buffer method for supplying a working fluid to a heat engine heater is known (Application for patent Ns 2015111076 dated 03/27/2015: BUFFER METHOD FOR SUBMITTING A WORKING BODY TO A HEATING ENGINE HEATER AND A DEVICE FOR ITS IMPLEMENTATION). A device is proposed in the form of a housing with a rotor installed inside it. In this case, the rotor cavities form buffer vessels. In this case, when the rotor rotates, each cavity is connected to one of the pairs of channels supplying and discharging the working fluid.

The disadvantage of the proposed device is the use of additional circulation fans necessary to ensure 15 circulation of the working fluid in the buffer device, in the combustion chamber and heat exchanger, which greatly complicates the engine as a whole, reduces its reliability and efficiency.

Another disadvantage of the proposed device is the high and sharp fluctuations in the pressure of the working fluid in the buffer vessels due to the 20 pressure differences in the supply channels to the combustion chamber, to the heat exchanger and to the source of the cooled working fluid, which leads to a decrease in the efficiency of circulation of the working fluid in the buffer device.

An object of the invention is to increase the efficiency of the 25 buffer device.

The problem is solved due to the fact that the rotor of the buffer device, consisting of a housing with a rotor installed inside it with the buffer cavities inside it, is made in the form of a centrifugal or axial rotor blade. In this case, buffer vessels are formed in the space between the rotor blades and the walls of the housing, and during rotation rotor circulation of the working fluid between the inlet and outlet channels is due to the driving force of the rotor blades.

Also, in order to ensure unidirectional flows of the working fluid in the buffer device, when the rotor rotates, the vessels connecting to the channel pairs in which the working fluid pressure is higher than in the vessels, are first connected to the channel supplying the working fluid, then the vessels are connected to the channel diverting the working fluid. As a result, the direction of flow of the working fluid is always directed from the channels leading into the working fluid. For the same purpose, when connecting vessels with pairs of channels, in which the pressure is lower than in the vessels, the vessels are first connected to the channel diverting the working fluid, then the vessels are connected to the channel supplying the working fluid.

In order to ensure maximum uniformity of the flow of the working fluid in the buffer device, it is proposed that the windows of the supply and outlet channels from the side where the beginning of their connection with the vessels is carried out be made at some angle to the blades. That provides a smoother expansion of the bore in the process of connecting the buffer vessels with the inlet and outlet channels. As a result, a more uniform balancing of the pressures in the buffer vessels and channels during their connection is ensured.

The figure 1 shows a schematic General view of a buffer device in section; figure 2 is a section aa in figure 1; figure 3 is a section bB in figure 2; figure 4 is a section bb in figure 2; figure 5 connection diagram of a buffer device; figure 6 is a multi-stage circuit buffer device; figure 7 is an example of a practical implementation of the device (in the context); figure 8 is a section aa in figure 7; Figure 9 is a sectional view of BB in Figure 7; figure 10 is a section bb in figure 7.

The buffer device with the centrifugal impeller of the rotor (Fig. 1) consists of a housing 1 and a cover 2 of the housing 1 with a rotor 4 installed inside it on the bearing 3. VI; VII; Viii. In the lid 2 the housing 1 there are supply channels I suitable to the inner perimeter of the rotor 4; II; III; IV.

The rotor 4 comprises impeller blades 5 mounted on it (hereinafter referred to as rotor blades) and a cover 6 covering them from above. Figure 5 shows a connection diagram of a buffer device.

Air (working fluid) through the air intake 7 enters through the supply channel II into the housing 1 of the buffer device, from where through the exhaust channel VIII the air enters the heat exchanger 8, then from the heat exchanger 8 the air enters the housing 1 of the buffer device through the supply channel IV, then air from the housing 1 of the buffer device enters through the exhaust channel V into the combustion chamber 9, where it mixes with the fuel and burns.

Combustion products (heated working fluid) from the combustion chamber 9 are divided into two streams. One stream enters the turbine 10, which gives off most of its potential energy, and leaves it into the atmosphere through the exhaust pipe 11. The second stream enters the casing 1 of the buffer device through the inlet channel I, then the combustion products from the casing 1 of the buffer device through the exhaust channel VII enter the heat exchanger 8, then the combustion products from the heat exchanger 8 enter the housing 1 of the buffer device through the inlet III, then the combustion products from the housing 1 of the buffer device through the exhaust channel l VI enters through the exhaust pipe 12 into the atmosphere. In this case, the heat exchanger 8 provides heat transfer from the combustion products coming from the combustion chamber 9 through the housing 1 of the buffer device to the atmosphere through the exhaust pipe 12 to the air (cooled working fluid) coming from the atmosphere through the air intake 7, through the housing 1 of the buffer device to the combustion chamber 9 .

Moreover, when the rotor 4 is rotated in the buffer device (figure 2) against the clockwise direction (working direction of rotation), continuous unidirectional flows of the working fluid from inlet channel I to outlet channel V; from II to VI; from III to VII; from IV to VIII. This ensures the replacement of the working fluid in the flows as follows:

When the rotor 4 is rotated in positions A, D, G, K, buffering of the working fluid is ensured, namely, the separation of the flows described above. 5 In this case, the angular width of sections A, D, G, K must be from one or more angular widths of space between two adjacent blades 5 of rotor 4.

In positions D, 3, the pressure is balanced in the buffer vessels and pairs of the outlet and inlet channels III, VII and II, VI, the pressure in which is lower than in the buffer vessels connected to them in this position, formed by the space between the blades 5 of rotor 4. In this case, the purpose of throttling the pressure balancing process is proposed (figure

3) the windows of the outlet channels VII, VI in these positions should be performed at a certain angle H to the blades 5 of the rotor 4 comprising from 1 to 80 angular degrees, depending on the operating conditions of the engine. Moreover, in these positions due to

15 expanded walls between the input channels I, III and channels III, II to the width GD and G-3 provide unidirectional throttling of the working fluid from the buffer vessels into the discharge channels VII, VI.

In positions B and L, pressure is balanced in the buffer vessels and pairs of the outlet and inlet channels I, V and IV, VIII, the pressure of which is 20 higher than in the buffer vessels connected to them in this position formed by the space between the blades 5 of the rotor 4. Moreover, with the purpose of throttling the pressure balancing process is proposed (figure

4) the windows of the supply channels VII, VI in these positions should be performed at a certain angle H to the blades 5 of the rotor 4, comprising from 1 to 80 angular degrees

25 depending on engine operating conditions. Moreover, in these positions due to the expanded walls between the output channels VI, VIII and channels VIII, V to the width K-L and AB, unidirectional throttling of the working fluid from the supply channels VIII, V to the buffer vessels is provided.

In positions B, E, I, M it is provided due to the driving force of the blades 5 of the rotor 4 that the buffer vessels are filled with a working fluid from the supply channels I; II; III; IV, while the working fluid already present in them comes from previous supply channels enters the discharge channels V; VI; VII; Viii. As a result, the working fluid from channel I enters into channel VII, from channel III enters into channel VI, from channel II enters into channel VIII, from channel IV enters into channel V. Moreover, the angular width of sections B, E, I, M has a width necessary and sufficient to ensure maximum efficiency of the replacement of the volume of the working fluid in the flows.

As a result, when the rotor 4 rotates, the buffer cavities formed by the space between the blades 5 of the rotor 4 pass through the following functional zones: A, D, G, K — buffer zone; B, L — pressure balancing zone with movement of the working fluid from the supply channel to the buffer cavity (buffer vessel), throttling zone; D, 3 — pressure balancing zone with the movement of the working fluid from the buffer cavity into the outlet channel, the throttling zone; B, E, I, M — zone of replacement of the working fluid in the flow between a pair of inlet and outlet channels by the working fluid from the buffer cavity.

An effective separation of the flows of the working fluid between pairs of inlet and outlet channels can be ensured only if the angular width of the buffer zone is greater than or equal to the angular width of the space between two adjacent rotor blades. Also, in order to reduce the deformation of the buffer device case due to the high temperature difference of the working fluid circulating in the buffer device, it is proposed to use a multistage-parallel circuit with many channels providing parallel operation of the set, from two or more connected in parallel functionally duplicating inlet and outlet channels (figure 6 ) Channels IA, 1B, IB are combined together in parallel and form a single channel I, channels HA, KB, HB form channel II, channels IIIA, SB, IIIB form channel III, channels IVA, IVB, IVB form channel IV, channels VA, VB VB form channel V, channels VIA, VIB, VIB form channel VI, channels VIIA, VIIB, VIIB form channel VII, channels VINA, VIIIB, VIIIB form channel VIII. AT As a result, during the operation of the proposed device, the temperature difference of the case will have a more local character - pass along the perimeter of the case.

The number of rotor blades in the buffer device can vary from one to a thousand or more. The rotor blades can be either straight or inclined in the above description, have an S-shaped profile and other known profiles of centrifugal fan impellers. In this case, the inlet and outlet channels are displaced relative to the center of rotation of the rotor by an angle equal to the angle of the radial turn of the rotor blades relative to this center.

Impellers of known axial fans and compressors are also possible. The flows of the working fluid in the device will run parallel to the axis of rotation of the impeller. The use of an axial impeller can significantly reduce the gaps between the impeller and the housing of the device, which increases the efficiency of the device. It is also possible to use other known types and types of impellers designed to move gases.

As well as in the known designs of centrifugal or axial fans, compressors, turbines, and in the buffer device, the need to use seals between the rotor and the housing of the device is also preserved, in order to reduce losses. Seals can be used as a labyrinth type, as well as other known types and types.

As an example of the practical implementation of the device, it is proposed to consider the design of a buffer device using an axial blade impeller (figure 7). The buffer device consists of a housing formed by the upper 13 and lower 14 by the walls of the housing and the ring 15 of the housing. Inside the bearings 3, a rotor 4 with blades 5 is installed. There are also four labyrinth seals 16. In figure 7, the arrows indicate the direction of flow of the working fluid when the rotor rotates counterclockwise (figure 8.9), which is the working direction of rotation. The figure 10 shows the rotor 4 with the blades 5 and the ring 15 of the housing. The supply channels are located around the circumference in the lower wall 14 of the housing. Outlet b the channels are located around the circumference in the upper wall 13 of the housing. The device has two rows of parallel, functionally identical sectors: A1, A2; B1, B2; B1, B2; P, G2; D1, D2; E1, E2; Ж1, Ж2; 31, 32; I1, I2; K1, K2; L1, L2; M1, M2. Moreover, the channel windows in these sectors have the same function as the centrifugal rotor buffer device described above.

Claims

F O R M U L A

1. Buffer device, consisting of a housing with inlet and outlet channels and with a rotor installed inside it with buffer tanks in it, characterized in that the rotor is made in the form of a blade impeller, and buffer tanks are formed by the space between the blades of the specified blade impeller (rotor blades ) and the walls of the housing, while the circulation of the working fluid in the buffer device is carried out by means of the driving force of the rotor blades.

2. The buffer device according to claim 1, characterized in that when connecting the buffer tank with a pair of inlet and outlet channels, the pressure of the working fluid in which is lower than in the buffer tank, the buffer tank is first connected to the discharge channel.

3. The buffer device according to claim 1, characterized in that when connecting the buffer tank with a pair of inlet and outlet channels, the pressure of the working fluid in which is higher than in the buffer tank, the buffer tank is first connected to the supply channel.

4. The buffer device according to claim 1, characterized in that the wall of the window of the outlet channel from the beginning of the connection of this channel with the buffer tank is located at an angle to the rotor blade.

5. The buffer device according to claim 1, characterized in that the wall of the window of the supply channel from the beginning of the connection of this channel with the buffer tank is at an angle to the rotor blade.

6. The buffer device according to claim 1, characterized in that a centrifugal impeller is used.

7. The buffer device according to claim 1, characterized in that the axial impeller is used.

8. The buffer device according to claim 1, characterized in that in the housing of the device there are many, from two or more, located around the circumference and connected in parallel functionally duplicating the input and output channels.

9. The buffer device according to claim 1 is characterized in that labyrinth type seals are used between the walls of the device body and the blade rotor.

10. The buffer device according to claim 1 is characterized in that the angular width of the buffer zone is greater than or equal to the angular width of the space between two adjacent rotor blades.

11. The buffer device according to claim 1 is characterized in that when using rotor blades rotated relative to the radial line, the inlet and outlet channels are offset relative to the center of rotation of the rotor by an angle equal to the angle of the radial turn of the outer and inner edges of the rotor blade relative to this center.