Compressor disk cavity cooling system

Abstract

The application discloses a compressor disc cavity cooling system which comprises a gas source, a compressor disc cavity and an ejector, a first branch and a second branch are connected to an outlet end of the gas source, the first branch is communicated with a first inlet of the ejector after passing through the compressor disc cavity, the second branch is communicated with a second inlet of the ejector, and the gas in the compressor disc cavity is sucked into the ejector through high-speed injection of the gas in the second inlet. In the compressor disc cavity cooling system, the exhaust end of the compressor disc cavity is communicated with the first inlet of the ejector, and the exhaust of the compressor disc cavity is assisted by the negative pressure generated by the high-speed jet flow, so that the gas supply and exhaust of the compressor disc cavity are simultaneously realized, the cooling effect of the compressor disc cavity is realized, and the leakage of the sealing position caused by the excessive internal pressure of the compressor disc cavity is avoided.

Description

Technical Field

[0001] This invention relates to a compressor disc cavity cooling system. Background Technology

[0002] For the rotating disk of a high-pressure compressor in an aero-engine, the disk temperature directly determines the strength constraints of the disk center, web, and other components. To reduce the impact of thermal stress on the rotating disk, cold air is typically introduced to cool the disk cavity. The cooling effect of the disk cavity is closely related to the internal flow conditions; however, the internal structure of the disk cavity is complex, with significant local drag losses, and centrifugal and radial Coriolis forces cause static pressure losses within the compressor disk cavity. Increasing the supply air pressure can improve the cooling effect of the disk cavity; however, increased pressure within the disk cavity can also lead to increased leakage at sealing points. Summary of the Invention

[0003] The technical problem to be solved by the present invention is to overcome the defect of the prior art that, while supplying air to the compressor disk cavity to cool the disk cavity, there is a risk of increased leakage at the sealing position, and to provide a compressor disk cavity cooling system.

[0004] The present invention solves the above-mentioned technical problems through the following technical solution:

[0005] This invention provides a compressor disk cooling system, which includes a gas source, a compressor disk, and an ejector. The outlet of the gas source is connected to a first branch and a second branch. The first branch passes through the compressor disk and connects to the first inlet of the ejector. The second branch connects to the second inlet of the ejector. By high-speed ejection of the gas introduced into the second inlet, the gas in the compressor disk is drawn into the ejector.

[0006] In this scheme, the above-mentioned structural form is adopted. The exhaust end of the compressor disk cavity is connected to the first air inlet of the ejector. The negative pressure generated by the high-speed jet assists the compressor disk cavity in exhausting, so as to simultaneously achieve air supply and exhaust for the compressor disk cavity. While achieving the cooling effect of the compressor disk cavity, it avoids the leakage at the sealing position from increasing due to excessive internal pressure of the compressor disk cavity.

[0007] Preferably, a first regulating valve is installed on the first branch, the first regulating valve being used to control the flow rate of the gas flowing in the first branch, and the first regulating valve being located between the gas source and the compressor disc cavity.

[0008] In this solution, the above-mentioned structure is adopted. By adjusting the opening of the first regulating valve, the air supply flow to the compressor plate cavity can be controlled. The air supply flow for cooling the compressor plate cavity can be adjusted according to the actual working conditions, which is highly flexible.

[0009] Preferably, on the first branch, a first pressure detector is installed between the first regulating valve and the compressor disk cavity, the first pressure detector being used to monitor the pressure of the gas flowing into the compressor disk cavity.

[0010] In this scheme, the above-mentioned structure is adopted. By checking the first pressure detector, the pressure of the gas flowing into the compressor disk cavity is monitored, thereby adjusting the opening of the first regulating valve so as to adjust the gas supply flow of the compressor disk cavity in real time.

[0011] Preferably, a second regulating valve is installed on the second branch, the second regulating valve being used to control the flow rate of the gas flowing in the second branch, the second regulating valve being located between the gas source and the ejector.

[0012] In this solution, the above-mentioned structure is adopted. By adjusting the opening of the second regulating valve, the flow rate of the high-speed fluid introduced into the ejector can be controlled, thereby adjusting the pumping flow rate of the compressor disk cavity according to the actual working conditions, which is highly flexible.

[0013] Preferably, on the first branch, a second pressure detector is installed between the compressor disk cavity and the ejector, the second pressure detector being used to monitor the pressure of the gas extracted from the compressor disk cavity.

[0014] In this scheme, the above-mentioned structure is adopted. By checking the second pressure detector, the pressure of the gas extracted from the compressor disk cavity is monitored, thereby adjusting the opening of the second regulating valve so as to adjust the gas extraction flow rate of the compressor disk cavity in real time.

[0015] Preferably, the first regulating valve is a solenoid valve;

[0016] And / or, the first pressure detector is a pressure gauge or a pressure sensor.

[0017] Preferably, the second regulating valve is a solenoid valve;

[0018] And / or, the second pressure detector is a pressure gauge or a pressure sensor.

[0019] Preferably, the ejector includes an ejector body, a first air inlet pipe, and a second air inlet pipe. The first air inlet pipe extends outward from the side wall of the ejector body and communicates with the ejector body. The second air inlet pipe extends into the interior of the ejector body from a first end. The first air inlet is located at the end of the first air inlet pipe away from the ejector body, and the second air inlet is located at the end of the second air inlet pipe away from the ejector body.

[0020] Preferably, the end of the second air inlet pipe that extends into the ejector body is closer to the first end than the connection point between the ejector body and the first air inlet pipe.

[0021] In this scheme, the above-mentioned structural form is adopted to enhance the ejector's ejection capability, thereby strengthening the auxiliary exhaust of the compressor disc cavity.

[0022] Preferably, the ejector body includes a receiving section, a tapering section, a mixing section, and an expanding section connected in sequence, the second air inlet pipe extends into the receiving section, the inner diameter of the tapering section gradually decreases from one end near the receiving section to one end near the mixing section, and the inner diameter of the expanding section gradually increases from one end near the mixing section to one end.

[0023] In this scheme, the above-mentioned structural form is adopted. The converging section reduces the resistance loss of the gas discharged from the compressor disk cavity and the gas flow in the second branch. Then, the two fluids enter the mixing section and are fully mixed in the mixing section to exchange energy. Then, the two fluids enter the expansion section, decelerate and pressurize, and then are discharged from the ejector.

[0024] Preferably, the inner diameter of the first end is denoted as D, the inner diameter of the first air inlet pipe is d1, the inner diameter of the second air inlet pipe is denoted as d2, and the distance between the end of the second air inlet pipe that extends into the ejector body and the connection point between the ejector body and the first air inlet pipe is denoted as L, where d2 / D = 1 / 3, D / d1 = 1, and L / d2 = 1.5.

[0025] In this scheme, the above-mentioned structural form is adopted, which further enhances the ejector's ejection capability, thereby further strengthening the auxiliary exhaust of the compressor disc cavity.

[0026] The positive and progressive effects of this invention are as follows:

[0027] In the compressor disk cooling system of the present invention, the exhaust end of the compressor disk is connected to the first air inlet of the ejector. The negative pressure generated by the high-speed jet assists the compressor disk in exhausting, so as to simultaneously supply and exhaust air to the compressor disk. While achieving the cooling effect of the compressor disk, it avoids the leakage at the sealing position from being too large due to excessive internal pressure of the compressor disk. Attached Figure Description

[0028] Figure 1 This is a schematic diagram of the compressor plate cooling system according to a preferred embodiment of the present invention.

[0029] Figure 2 This is a schematic diagram of the ejector structure according to a preferred embodiment of the present invention.

[0030] Figure 3This is a simplified schematic diagram of the ejector according to a preferred embodiment of the present invention.

[0031] Explanation of reference numerals in the attached figures:

[0032] Gas source 1

[0033] First Branch Road 2

[0034] Second Branch Road 3

[0035] Compressor disc cavity 4

[0036] ejector 5

[0037] First air intake pipe 51

[0038] First air intake 511

[0039] Second air intake pipe 52

[0040] Second air intake 521

[0041] Ejector body 53

[0042] First end 531

[0043] Receive Section 532

[0044] tapering segment 533

[0045] Mixed Section 534

[0046] Expansion section 535

[0047] First regulating valve 6

[0048] First pressure detector 7

[0049] Second regulating valve 8

[0050] Second pressure detector 9 Detailed Implementation

[0051] The present invention will be further illustrated by way of embodiments below, but the present invention is not limited to the scope of the following embodiments.

[0052] This invention provides a compressor disc cooling system; please also refer to... Figure 1 , Figure 2 and Figure 3The compressor disk cooling system includes an air source 1, a compressor disk 4, and an ejector 5. The outlet of the air source 1 is connected to a first branch 2 and a second branch 3. The first branch 2 passes through the compressor disk 4 and is connected to the first air inlet 511 of the ejector 5. The second branch 3 is connected to the second air inlet 521 of the ejector 5. Through the high-speed ejection of the gas introduced into the second air inlet 521, the gas in the compressor disk 4 is drawn into the ejector 5. Gas source 1 supplies gas to compressor disk cavity 4 through first branch 2 to cool compressor disk cavity 4; simultaneously, gas source 1 introduces high-speed fluid into second inlet 521 through second branch 3. Due to the turbulent diffusion effect of the jet, the gas entrained in compressor disk cavity 4 enters ejector 5 through first inlet 511. The gas discharged from compressor disk cavity 4 and the gas in second branch 3 mix and exchange energy inside ejector 5. The high-temperature gas discharged from compressor disk cavity 4 is ejected and cooled in ejector 5 before being discharged. Figure 2 and Figure 3 The straight lines and curved lines with arrows inside the ejector 5 indicate the airflow direction. The exhaust end of the compressor disk cavity 4 is connected to the first air inlet 511 of the ejector 5. The negative pressure generated by the high-speed jet assists the exhaust of the compressor disk cavity 4, so as to simultaneously supply and exhaust air to the compressor disk cavity 4. While achieving the cooling effect of the compressor disk cavity 4, it avoids the increase of leakage at the sealing position due to excessive internal pressure of the compressor disk cavity 4.

[0053] like Figure 1 As shown, a first regulating valve 6 is installed on the first branch 2. The first regulating valve 6 is used to control the flow rate of the gas flowing in the first branch 2. The first regulating valve 6 is located between the gas source 1 and the compressor disk cavity 4. By adjusting the opening of the first regulating valve 6, the flow rate of gas supplied to the compressor disk cavity 4 can be controlled. The flow rate of gas supplied to cool the compressor disk cavity 4 can be adjusted according to the actual working conditions, which is highly flexible.

[0054] In this embodiment, as Figure 1 As shown, a first pressure detector 7 is installed between the first regulating valve 6 and the compressor cavity 4 on the first branch 2. The first pressure detector 7 is used to monitor the pressure of the gas flowing into the compressor cavity 4. By monitoring the pressure of the gas flowing into the compressor cavity 4 by checking the first pressure detector 7, the opening of the first regulating valve 6 is adjusted to adjust the air supply flow rate of the compressor cavity 4 in real time. Specifically, a threaded connection port is provided on the first branch 2 for the threaded connection of the first pressure detector 7 to the first branch 2.

[0055] like Figure 1As shown, a second regulating valve 8 is installed on the second branch 3. The second regulating valve 8 is used to control the flow rate of the gas flowing in the second branch 3. The second regulating valve 8 is located between the gas source 1 and the ejector 5. By adjusting the opening of the second regulating valve 8, the flow rate of the high-speed fluid introduced into the ejector 5 is controlled, thereby adjusting the pumping flow rate of the compressor disk cavity 4 according to the actual working conditions, which is highly flexible.

[0056] In this embodiment, a second pressure detector 9 is installed on the first branch 2 between the compressor disk cavity 4 and the ejector 5. The second pressure detector 9 is used to monitor the pressure of the gas extracted from the compressor disk cavity 4. By monitoring the pressure of the gas extracted from the compressor disk cavity 4 by checking the second pressure detector 9, the opening of the second regulating valve 8 is adjusted to adjust the gas extraction flow rate of the compressor disk cavity 4 in real time. Specifically, a threaded connection port is provided on the second branch 3 to realize the threaded connection between the second pressure detector 9 and the second branch 3.

[0057] The first regulating valve 6 is a solenoid valve, which can be remotely controlled to control the air supply flow rate of the compressor chamber 4, facilitating operation. Alternatively, the first pressure detector 7 can be a pressure gauge or a pressure sensor. Alternatively, the first regulating valve 6 can be a solenoid valve, and the first pressure detector 7 can be a pressure gauge or a pressure sensor.

[0058] The second regulating valve 8 is a solenoid valve, which can be remotely controlled to control the air flow rate of the compressor chamber 4, facilitating operation. Alternatively, the second pressure detector 9 can be a pressure gauge or a pressure sensor. Alternatively, the second regulating valve 8 can be a solenoid valve, and the second pressure detector 9 can be a pressure gauge or a pressure sensor.

[0059] In other embodiments, the first regulating valve 6 can also adjust the opening size of the first branch 2 through a mechanical structure, and the second regulating valve 8 can also adjust the opening size of the second branch 3 through a mechanical structure to facilitate local operation.

[0060] like Figure 2 and Figure 3 As shown, the ejector 5 includes an ejector body 53, a first air inlet pipe 51, and a second air inlet pipe 52. The first air inlet pipe 51 extends outward from the side wall of the ejector body 53 and communicates with the ejector body 53. The second air inlet pipe 52 extends into the interior of the ejector body 53 from the first end 531 of the ejector body 53. The first air inlet 511 is located at the end of the first air inlet pipe 51 away from the ejector body 53, and the second air inlet 521 is located at the end of the second air inlet pipe 52 away from the ejector body 53.

[0061] The end of the second air inlet pipe 52 that extends into the ejector body 53 is closer to the first end 531 than the connection point between the ejector body 53 and the first air inlet pipe 51. Please refer to... Figure 3 To understand this, one end of the second intake pipe 52 that extends into the ejector body 53 is located to the left of the connection between the ejector body 53 and the first intake pipe 51. This structural design enhances the ejection capability of the ejector 5, thereby strengthening the auxiliary exhaust to the compressor disc cavity 4. Specifically, when the end of the second air inlet pipe 52 that extends into the ejector body 53 is closer to the first end 531 than the connection point between the ejector body 53 and the first air inlet pipe 51, the ejection ratio can reach more than 1.5. The ejection ratio is the ratio of the mass flow rate of the ejector fluid (lower pressure) in the ejector 5 to the mass flow rate of the working fluid (higher pressure), that is, the ratio of the mass flow rate of the fluid sucked away from the compressor, i.e., the disc cavity 4, to the mass flow rate of the high-speed fluid entering the second air inlet 521. When the end of the second air inlet pipe 52 that extends into the ejector body 53 is farther away from the first end 531 than the connection point between the ejector body 53 and the first air inlet pipe 51, the ejection ratio decreases sharply to about 0.84.

[0062] like Figure 2 As shown, the ejector body 53 includes a receiving section 532, a converging section 533, a mixing section 534, and an expanding section 535 connected in sequence. The second inlet pipe 52 extends into the receiving section 532. The inner diameter of the converging section 533 gradually decreases from the end near the receiving section 532 to the end near the mixing section 534. The inner diameter of the expanding section 535 gradually increases from the end near the mixing section 534 to the outer end. The converging section 533 reduces the resistance loss when the gas discharged from the compressor disk cavity 4 flows into the second branch 3. Then, the two fluids enter the mixing section 534 and are fully mixed to exchange energy. After that, the two fluids enter the expanding section 535, where they are decelerated and pressurized, and then discharged from the ejector 5.

[0063] like Figure 3 As shown, the inner diameter of the first end 531 is denoted as D, the inner diameter of the first intake pipe 51 is d1, the inner diameter of the second intake pipe 52 is denoted as d2, and the distance between the end of the second intake pipe 52 extending into the ejector body 53 and the connection point between the ejector body 53 and the first intake pipe 51 is denoted as L. Where d2 / D = 1 / 3, D / d1 = 1, and L / d2 = 1.5. This structural form further enhances the ejection capability of the ejector 5, thereby further strengthening the auxiliary exhaust to the compressor disk cavity 4. Specifically, the angle between the first intake pipe 51 and the ejector body 53 is 45°. Based on a working gas pressure of 3 bar and an ejector gas pressure of 1 bar, the working gas flow rate, ejector gas flow rate, and ejection ratio are shown in the table below for different values ​​of d2 / D, D / d1, and L / d2.

[0064]

[0065] While specific embodiments of the present invention have been described above, those skilled in the art should understand that these are merely illustrative examples, and the scope of protection of the present invention is defined by the appended claims. Those skilled in the art can make various changes or modifications to these embodiments without departing from the principles and essence of the present invention, but all such changes and modifications fall within the scope of protection of the present invention.

Claims

1. A compressor disc cooling system, characterized in that, The compressor disk cooling system includes a gas source, a compressor disk, and an ejector. The outlet of the gas source is connected to a first branch and a second branch. The first branch passes through the compressor disk and connects to the first inlet of the ejector. The second branch connects to the second inlet of the ejector. By high-speed ejection of the gas introduced into the second inlet, the gas in the compressor disk is drawn into the ejector.

2. The compressor disc cooling system as described in claim 1, characterized in that, A first regulating valve is installed on the first branch. The first regulating valve is used to control the flow rate of the gas flowing in the first branch. The first regulating valve is located between the gas source and the compressor disc cavity.

3. The compressor disc cooling system as described in claim 2, characterized in that, On the first branch, a first pressure detector is installed between the first regulating valve and the compressor disk cavity. The first pressure detector is used to monitor the pressure of the gas flowing into the compressor disk cavity.

4. The compressor disc cooling system as described in claim 1, characterized in that, A second regulating valve is installed on the second branch. The second regulating valve is used to control the flow rate of the gas flowing in the second branch. The second regulating valve is located between the gas source and the ejector.

5. The compressor disc cooling system as described in claim 4, characterized in that, On the first branch, a second pressure detector is installed between the compressor disk cavity and the ejector. The second pressure detector is used to monitor the pressure of the gas extracted from the compressor disk cavity.

6. The compressor disc cooling system as described in claim 3, characterized in that, The first regulating valve is a solenoid valve; And / or, the first pressure detector is a pressure gauge or a pressure sensor.

7. The compressor disc cooling system as described in claim 5, characterized in that, The second regulating valve is a solenoid valve; And / or, the second pressure detector is a pressure gauge or a pressure sensor.

8. The compressor disc cooling system as described in claim 1, characterized in that, The ejector includes an ejector body, a first air inlet pipe, and a second air inlet pipe. The first air inlet pipe extends outward from the side wall of the ejector body and communicates with the ejector body. The second air inlet pipe extends into the interior of the ejector body from a first end. The first air inlet is located at the end of the first air inlet pipe away from the ejector body, and the second air inlet is located at the end of the second air inlet pipe away from the ejector body.

9. The compressor disc cooling system as described in claim 8, characterized in that, The end of the second air inlet pipe that extends into the ejector body is closer to the first end than the connection point between the ejector body and the first air inlet pipe.

10. The compressor disc cooling system as described in claim 8, characterized in that, The ejector body includes a receiving section, a tapering section, a mixing section, and an expanding section connected in sequence. The second air inlet pipe extends into the receiving section. The inner diameter of the tapering section gradually decreases from one end near the receiving section to one end near the mixing section. The inner diameter of the expanding section gradually increases from one end near the mixing section to one end near the outer end.

11. The compressor disc cooling system as described in claim 8, characterized in that, The inner diameter of the first end is denoted as D, the inner diameter of the first air inlet pipe is d1, the inner diameter of the second air inlet pipe is denoted as d2, and the distance between the end of the second air inlet pipe that extends into the ejector body and the connection point between the ejector body and the first air inlet pipe is denoted as L, where d2 / D = 1 / 3, D / d1 = 1, and L / d2 = 1.5.

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