Two-stage super-speed centrifugal refrigeration compressor with variable angle low consistency diffuser structure

Abstract

The utility model relates to centrifugal compressor refrigeration equipment field, a two -stage super -high -speed centrifugal refrigeration compressor with variable angle low consistency diffuser structure. Two -stage super -high -speed centrifugal refrigeration compressor includes two -stage symmetrical arrangement's compression structure, specifically including impeller, diffuser, press shell and end plate. The diffuser includes adjustable angle blade, and it is evenly distributed along the circumference, and the blade consistency at the import is less than or equal to 0.8. When the compressor operating condition changes, two -stage impeller outlet airflow angle will change, at this moment can pass through the adjustment diffuser blade angle, adaptation airflow angle's change. The utility model widens the operating range of compressor to adapt more refrigeration working condition, reduces the aerodynamic loss again, improves the whole machine aerodynamic efficiency.

Description

Technical Field

[0001] This utility model generally relates to the field of centrifugal compressor refrigeration equipment, and more specifically, it relates to a two-stage ultra-high-speed centrifugal refrigeration compressor with a variable-angle low-consistency diffuser structure. Background Technology

[0002] With the rapid development of digital technology and the continuous expansion of data centers, numerous servers operate continuously, generating extremely high levels of heat. Energy-efficient equipment is needed for cooling to maintain server operation. In the new energy field, energy storage devices are increasingly widely used. These devices also generate significant heat during charging and discharging, requiring effective heat dissipation and cooling measures. Ultra-high-speed centrifugal compressors, due to their small size and high cooling efficiency, are widely used in data center cooling and heat dissipation during the charging and discharging of energy storage devices. Traditional ultra-high-speed centrifugal compressors typically use either bladeless diffusers or fixed-angle blade diffusers to ensure a sufficiently wide operating range. When using a bladeless diffuser, the compressor has a wide operating range, but the significant aerodynamic losses in the bladeless section result in low overall aerodynamic efficiency. When using a fixed-angle blade diffuser, the compressor has a narrow operating range, but its aerodynamic efficiency at the rated operating point is higher than that of compressors with bladeless diffusers. Utility Model Content

[0003] Based on existing technology, the objective of this utility model is to provide a two-stage ultra-high-speed centrifugal refrigeration compressor with a variable-angle low-density diffuser structure, which can adapt to more different refrigeration conditions and improve the aerodynamic efficiency of the compressor.

[0004] According to this invention, the above-mentioned task is accomplished by a two-stage ultra-high-speed centrifugal refrigeration compressor with a variable-angle, low-consistency diffuser structure. The ultra-high-speed centrifugal refrigeration compressor includes: A first compression structure, configured to perform a first compression of the gas, and disposed on a first side of the compressor, wherein the first compression structure includes a first diffuser; and A second compression structure, configured to compress the gas a second time, is arranged on a second side opposite to the first side. The second compression structure includes a second diffuser. The first and second diffusers include circumferentially distributed blades and are configured to diffuse the incoming gas. The consistency at the inlet of the first diffuser and / or the second diffuser is set to be less than or equal to 0.8.

[0005] Furthermore, the blades of the first diffuser and the second diffuser are configured as variable-angle blades; and / or The blade angles of the first diffuser and the second diffuser can be adjusted according to the operating conditions of the compressor to adapt to changes in the airflow angle and reduce airflow impact losses.

[0006] Furthermore, the first compression structure also includes: The first impeller is configured to perform initial work on the incoming gas; A first pressure chamber, configured to guide and deliver gas within the first compression structure; and The first end plate is configured to be connected to the first pressure shell.

[0007] Furthermore, the first diffuser is arranged on the outlet side of the first impeller and connected to the first end plate, and is configured to receive and diffuse the gas after the first impeller has done work.

[0008] Furthermore, the second compression structure also includes: The second impeller is configured to perform secondary work on the gas after the initial diffusion. A second pressure chamber, configured to guide and deliver gas within the second compression structure; and The second end plate is configured to connect to the second pressure shell.

[0009] Furthermore, the second diffuser is arranged on the outlet side of the second impeller and connected to the second end plate, and is configured to receive and diffuse the gas after it has been worked on by the second impeller.

[0010] Furthermore, the ultra-high-speed centrifugal refrigeration compressor also includes: A motor stator assembly, configured as the stator portion for motor operation, and connected to the first end plate and the second end plate; and The main shaft is arranged in the center of the compressor and is connected to the first impeller and the second impeller.

[0011] Furthermore, the main shaft, together with the first impeller and the second impeller, forms a rotor assembly. The main shaft, driven by the motor stator assembly, forms a drive structure, which drives the rotor assembly to rotate synchronously under the action of the motor.

[0012] Furthermore, the ultra-high-speed centrifugal refrigeration compressor also includes an intermediate tube, which is configured to connect the first compression structure and the second compression structure.

[0013] One end of the intermediate tube is connected to the outlet end of the first pressure shell, and the other end is connected to the inlet end of the second impeller, so as to directionally transport the gas processed by the first compression structure to the inlet of the second compression structure.

[0014] This invention proposes a two-stage ultra-high-speed centrifugal refrigeration compressor with a variable-angle, low-consistency diffuser structure, which has at least the following beneficial effects: First, the two-stage diffuser of this invention adopts an adjustable-angle blade design, which can adapt to changes in the impeller outlet airflow angle when the operating conditions change by adjusting the blade angle. Combined with the low-consistency design of the blades at the inlet (consistency less than or equal to 0.8), this not only broadens the compressor's operating range to adapt to more refrigeration conditions but also reduces aerodynamic losses and improves the overall aerodynamic efficiency. Second, the two-stage symmetrical compression structure enables sufficient work and diffusion of the gas through a two-stage continuous compression process: initial work by the first impeller, initial diffusion by the first diffuser, followed by secondary work by the second impeller and secondary diffusion by the second diffuser. This improves the degree of gas compression and stability. Attached Figure Description

[0015] To further illustrate the advantages and other features of the various embodiments of this utility model, a more specific description of the embodiments of this utility model will be presented with reference to the accompanying drawings. It is understood that these drawings depict only typical embodiments of this utility model and are therefore not intended to limit its scope. In the drawings, for clarity, the same or corresponding parts will be indicated by the same or similar reference numerals.

[0016] Figure 1 A cross-sectional view of a two-stage ultra-high-speed centrifugal refrigeration compressor with a variable-angle low-consistency diffuser structure is shown in one embodiment of the present invention.

[0017] Figure 2 A schematic diagram of a low-consistency diffuser with a variable angle is shown in one embodiment of the present invention.

[0018] Figure 3 A schematic diagram of the blades of a low-consistency diffuser with a variable angle is shown in one embodiment of the present invention.

[0019] List of reference numerals 100 Two-stage ultra-high-speed centrifugal refrigeration compressor 1 Second pressure shell 2 Second end plate 3. Intermediate pipe 4 Second impeller 5. Motor stator assembly 6 First end plate 7 First pressure shell 8 First impeller 9 Second diffuser 10 First diffuser 11 Spindle 12 blades Detailed Implementation The present invention will be further described below with reference to the accompanying drawings and specific embodiments. It should be noted that the components in the drawings may be shown exaggeratedly for illustrative purposes and are not necessarily to scale.

[0020] In this utility model, the various embodiments are merely intended to illustrate the solution of this utility model and should not be construed as limiting.

[0021] In this utility model, unless otherwise specified, the quantifiers “one” and “one” do not exclude scenarios involving multiple elements.

[0022] It should also be noted that in the embodiments of this utility model, only a portion of the parts or components may be shown for clarity and simplicity. However, those skilled in the art will understand that, under the teachings of this utility model, the required parts or components can be added according to the specific scenario.

[0023] It should also be noted that in the description of this utility model, the terms "center," "longitudinal," "lateral," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," and "outer," etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are used only for the convenience of describing this utility model and for simplifying the description, and do not explicitly or implicitly suggest that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this utility model. Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance.

[0024] In this utility model, unless otherwise specified, the terms "outlet" and "inlet" refer to the parts where gas flows out and flows in.

[0025] The present invention will be further described below with reference to the accompanying drawings and specific embodiments.

[0026] Figure 1 A cross-sectional view of a two-stage ultra-high-speed centrifugal refrigeration compressor with a variable-angle low-consistency diffuser structure is shown in one embodiment of the present invention. Figure 1As shown, the two-stage ultra-high-speed centrifugal refrigeration compressor comprises a second pressure shell 1, a second end plate 2, an intermediate tube 3, a second impeller 4, a motor stator assembly 5, a first end plate 6, a first pressure shell 7, a first impeller 8, a second diffuser 9, a first diffuser 10, and a main shaft 11. The second impeller 4 and the first impeller 8 are respectively mounted on both sides of the motor main shaft 11, together forming the rotor assembly. The first end plate 6 is connected to the motor stator assembly 5, and the first pressure shell 7 is connected to the first end plate 6. The second end plate 2 is connected to the motor stator assembly 5, the second pressure shell 1 is connected to the second end plate 2, the second diffuser 9 is mounted on the second end plate 2, and the first diffuser 10 is mounted on the first end plate 6.

[0027] The first end plate 6, the first pressure shell 7, the first impeller 8, and the first diffuser 10 together constitute the first compression structure; the second end plate 2, the second pressure shell 1, the second impeller 4, and the second diffuser 9 together constitute the second compression structure. The dual compression structure performs sufficient work and compression on the gas.

[0028] The functions of each component in a two-stage ultra-high-speed centrifugal refrigeration compressor with a variable-angle low-consistency diffuser structure are described below: The first end plate 6 and the second end plate 2 are configured to provide mounting bases for other components; The first impeller 8 and the second impeller 4 are configured to rotate and do work on the incoming gas, compressing the gas; First diffuser 10 and second diffuser 9 are configured to diffuse the gas after the impeller has done work. The first pressure shell 7 and the second pressure shell 1 are configured to guide the flow direction of the diffused airflow. Intermediate tube 3 is configured to connect the first compression structure and the second compression structure; Motor stator assembly 5, configured to drive the motor rotor portion to rotate; and The main shaft 11 is configured to mount the first impeller 8 and the second impeller 4, which together constitute the rotor assembly.

[0029] The working principle of this utility model is briefly described below: When the drive motor is running, the gas flows along... Figure 1 The gas enters the compressor 100 in the direction of the arrow, is first worked by the first impeller 8, and then diffused by the first diffuser 10. After that, it is transported to the inlet of the second impeller 4 through the first pressure shell 7 and the intermediate pipe 3. Then, the second impeller 4 continues to work on the gas, and then it is diffused by the second diffuser 9. Finally, it is discharged in the direction of the arrow through the outlet of the second pressure shell 1, completing the two-stage compression work of the gas.

[0030] Figure 2This diagram illustrates a low-consistency diffuser with a variable angle in one embodiment of the present invention, specifically a schematic diagram of the structure of the first diffuser 10 and the second diffuser 9. Figure 2 As shown, the diffuser includes multiple blades 12 that are evenly distributed circumferentially, and the overall edge of the diffuser has a circular outline. The consistency at the diffuser inlet is less than 0.8, making it a low-consistency diffuser.

[0031] Diffuser consistency, also known as diffuser blade consistency, is a key parameter describing the density of diffuser blade arrangement. It is defined as the ratio of blade chord length to blade pitch, and the calculation formula is as follows: Wherein, blade chord length (b) refers to the length of the blade along the chord direction (usually the straight-line distance from the leading edge to the trailing edge of the blade, i.e., the "width" of the blade); blade pitch (t) refers to the circumferential distance between corresponding points of two adjacent blades (usually calculated as the arc length spacing on the circumference of the blade's rotation). When the diffuser consistency is less than 0.9, it can be defined as a low-consistency diffuser.

[0032] The following explains the definitions of the diffuser's inlet and outlet: The core of a bladed diffuser is a ring of blades arranged circumferentially, which form multiple diffusion channels. The inlet refers to the section of the blades near the diffuser inlet (i.e., the side adjacent to the impeller outlet), and its function is: The high-speed airflow from the impeller is guided smoothly into the diffuser channel. By matching the direction of the airflow at the impeller outlet with the blade inlet angle, the "impact loss" is reduced. If the blade inlet angle does not match the airflow direction, the airflow will collide with the leading edge of the blade, forming vortices and energy loss.

[0033] In short, the inlet is the first point of contact between the airflow and the diffuser blades, and the shape and angle of the blades directly affect the initial guiding effect of the airflow.

[0034] The section of the same set of blades near the diffuser outlet (i.e., the side adjacent to subsequent components such as the volute and recirculator) can be called the outlet. Its function is: Controlling the direction and speed of airflow at the diffuser outlet ensures that the airflow flows into the next stage component at the designed angle (e.g., the volute requires the airflow to enter evenly along the circumference, while the return flow requires the airflow to be turned to enter the next stage impeller). In conjunction with the expansion design of the diffuser channel, the conversion of kinetic energy into static pressure energy is completed, so that the outlet airflow parameters (pressure, velocity) meet the requirements of subsequent processes.

[0035] Figure 3 A schematic diagram of the blades of a low-consistency diffuser with a variable angle is shown in one embodiment of the present invention. Figure 3As shown, the blades are rotatably fixed to the shaft.

[0036] like Figure 2 and Figure 3 As shown, when the compressor's operating conditions change, the airflow angle at the outlet of the two-stage impeller will change. At this time, the aerodynamic efficiency can be improved by adjusting the size of the diffuser blade angle βa to adapt to the change in airflow angle.

[0037] Compared to conventional bladed diffusers, low-density bladed diffusers have fewer blades and relatively lower aerodynamic efficiency near the design point, but offer a wider stable operating range. Compared to bladeless diffusers, they have lower airflow losses and higher aerodynamic efficiency near the design point. Therefore, a variable-angle low-density bladed diffuser in one embodiment of this invention can simultaneously ensure higher aerodynamic efficiency and a wider stable operating range.

[0038] Although various embodiments of the present invention have been described above, it should be understood that they are presented by way of example only and not as limitations. It will be apparent to those skilled in the art that various combinations, modifications, and alterations can be made without departing from the spirit and scope of the present invention. Therefore, the breadth and scope of the present invention disclosed herein should not be limited by the exemplary embodiments disclosed above, but should be defined solely by the appended claims and their equivalents.

Claims

1. A two-stage ultra-high-speed centrifugal refrigeration compressor with a variable-angle low-consistency diffuser structure, characterized in that, include: A first compression structure, configured to compress a gas for the first time, and disposed on a first side of the compressor, wherein the first compression structure includes a first diffuser; as well as A second compression structure, configured to compress the gas a second time, is arranged on a second side opposite to the first side. The second compression structure includes a second diffuser. The first and second diffusers include circumferentially distributed blades and are configured to diffuse the incoming gas. The consistency at the inlet of the first diffuser and / or the second diffuser is set to be less than or equal to 0.

8.

2. The compressor according to claim 1, characterized in that, The blades of the first diffuser and the second diffuser are configured as variable-angle blades; and / or The blade angles of the first diffuser and the second diffuser can be adjusted according to the operating conditions of the compressor to adapt to changes in the airflow angle and reduce airflow impact losses.

3. The compressor according to claim 1, characterized in that, The first compression structure further includes: The first impeller is configured to perform initial work on the incoming gas; A first pressure chamber, configured to guide and deliver gas within the first compression structure; and The first end plate is configured to be connected to the first pressure shell.

4. The compressor according to claim 3, characterized in that, The first diffuser is located at the outlet side of the first impeller and connected to the first end plate. It is configured to receive and diffuse the gas after it has been worked on by the first impeller.

5. The two-stage ultra-high-speed centrifugal refrigeration compressor according to claim 3, characterized in that, The second compression structure also includes: The second impeller is configured to perform secondary work on the gas after the initial diffuser. A second pressure chamber, configured to guide and deliver gas within the second compression structure; and The second end plate is configured to connect to the second pressure shell.

6. The compressor according to claim 5, characterized in that, The second diffuser is arranged on the outlet side of the second impeller and connected to the second end plate. It is configured to receive the gas after the second impeller has done work and diffuse it.

7. The compressor according to claim 5, characterized in that, Also includes: A motor stator assembly, configured as the stator portion for motor operation, and configured to connect to the first end plate and the second end plate; as well as The main shaft is arranged in the center of the compressor and is configured to connect with the first impeller and the second impeller.

8. The compressor according to claim 7, characterized in that, The main shaft, together with the first impeller and the second impeller, forms a rotor assembly. The main shaft, driven by the motor stator assembly, forms a drive structure, which drives the rotor assembly to rotate synchronously under the action of the motor.

9. The compressor according to claim 7, characterized in that, It also includes an intermediate tube configured to connect the first compression structure and the second compression structure.

10. The compressor according to claim 9, characterized in that, One end of the intermediate tube is connected to the outlet end of the first pressure shell, and the other end is connected to the inlet end of the second impeller, so as to directionally transport the gas processed by the first compression structure to the inlet of the second compression structure.

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