Fan structure for small-temperature-rise centrifugal vapor compression device

Abstract

The invention relates to a fan structure for a small temperature rise centrifugal vapor compression device, and relates to the technical field of vapor compression, the fan structure comprises a volute, a main shaft body is rotatably arranged in the volute, the main shaft body is sleeved with a hub body, the hub body is sleeved with a front disc body and a rear disc body, and the main shaft body, the hub body, the front disc body and the rear disc body are coaxially arranged; a plurality of blades are welded among the front disc body, the rear disc body and the hub body, an air seal seat is arranged between the volute and the main shaft body and located on the side, away from the front disc body, of the rear disc body, a plurality of large auxiliary blades and a plurality of small auxiliary blades are fixedly arranged on the side, away from the blades, of the rear disc body, and the large auxiliary blades are located on the sides, away from the hub body, of the small auxiliary blades. A plurality of trapezoidal grooves are formed in the front disc body, and the number of the trapezoidal grooves is consistent with that of the blades. The impeller has the effects of reducing the failure rate of matched operation of the impeller and the main shaft and improving the matched operation stability of the impeller and the main shaft.

Description

Technical Field

[0001] The invention relates to the technical field of steam compression, in particular to a fan structure for a small temperature rise centrifugal steam compression device. Background Art

[0002] MVR technology uses the secondary steam generated by the evaporation system and the mechanical energy of the compressor to convert the low-grade secondary steam into a high-grade steam heat source, thereby replacing the traditional fresh steam, thereby achieving efficient recycling of steam and its energy. With the continuous improvement of global requirements for environmental protection and energy conservation, MVR system technology has been widely used in food, pharmaceuticals, chemicals, and wastewater treatment. Among them, the steam compressor is the core equipment of the MVR system.

[0003] At present, the steam compressor has a similar structure to the traditional D-type fan, with a single cantilever structure. The impeller and the main shaft are connected by an interference fit, and the impeller diameter is usually designed to be larger to meet the large flow steam demand. During the operation of the impeller and the main shaft, the axial additional force generated by the air pressure is large, which increases the axial force on the bearing, easily causing problems such as leakage of the steam medium and deformation of the impeller outlet, resulting in abnormal operation between the impeller and the main shaft. Summary of the invention

[0004] In order to reduce the failure rate of the coordinated operation of the impeller and the main shaft and improve the stability of the coordinated operation of the impeller and the main shaft, the present application provides a fan structure for a small temperature rise centrifugal steam compression device.

[0005] The fan structure for a small temperature rise centrifugal steam compression device provided in the present application adopts the following technical solution: A fan structure for a small temperature-rise centrifugal steam compression device comprises a volute, a main shaft body is rotatably arranged in the volute, a hub body is sleeved on the main shaft body, a front disc body and a rear disc body are sleeved on the hub body, the main shaft body, the hub body, the front disc body and the rear disc body are coaxially arranged, a plurality of blades are welded between the front disc body, the rear disc body and the hub body, an air seal seat is arranged between the volute and the main shaft body, the air seal seat is located on the side of the rear disc body away from the front disc body, a plurality of large auxiliary blades and a plurality of small auxiliary blades are fixedly arranged on the side of the rear disc body away from the blades, the large auxiliary blades are located on the side of the small auxiliary blades away from the hub body, a plurality of trapezoidal grooves are provided on the front disc body, and the number of the trapezoidal grooves is consistent with the number of blades.

[0006] By adopting the above technical scheme, in the process of the main shaft driving the blades to rotate, the large auxiliary blades offset the axial force generated by the operation of the blades and reduce the vibration of the main shaft. The small auxiliary blades generate negative pressure at the hub body and reduce the positive pressure at the gas seal seat, thereby reducing the leakage of the steam medium. The trapezoidal grooves and the blade outlets are staggered to reduce excessive deformation at the impeller outlet, reduce the failure rate of the coordinated operation of the impeller and the main shaft, and improve the stability of the coordinated operation of the impeller and the main shaft.

[0007] Preferably, the blades are of a quasi-three-dimensional arc structure, the blades are evenly distributed along the circumferential direction, the rear disc body is of a circular plate structure, the outer diameter of the rear disc body is the same as the outer diameter of the front disc body, the hub body is a forged cylindrical structure, a number of triangular reinforcement ribs are welded between the hub body and the rear disc body, a cone disc is jointly sleeved on the triangular reinforcement ribs, and the hub body, rear disc body and blades are all welded to the cone disc.

[0008] By adopting the above technical solution, the blades, rear disc body, front disc body, hub body, triangular reinforcement ribs and cone disc together form an impeller, so that the impeller adopts advanced cavity geometry design, which ensures the efficient aerodynamic performance of the impeller while reducing the manufacturing cost of the impeller.

[0009] Preferably, the front disk body comprises a front disk inlet ring, a front disk connecting ring and a front disk outlet ring, one end of the front disk connecting ring is welded to the front disk inlet ring, and the other end of the front disk connecting ring is welded to the front disk outlet ring, the front disk inlet ring is located on the side of the front disk outlet ring away from the rear disk body, the front disk inlet ring, the front disk connecting ring and the front disk outlet ring are all welded to the blades, the front disk inlet ring, the front disk connecting ring and the front disk outlet ring are all fitted with the blades, an impeller inlet is formed between the blades, the front disk inlet ring and the hub body, and an impeller outlet is formed between the blades, the front disk outlet ring and the rear disk body.

[0010] By adopting the above technical solution, the front disc inlet ring is fitted with the impeller inlet curve, and the front disc outlet ring is fitted with the impeller outlet curve, so as to ensure the smooth flow of airflow inside the impeller.

[0011] Preferably, the thickness of the front disc inlet ring is the same as that of the front disc outlet ring, and both are smaller than the thickness of the front disc connecting ring. A front disc reinforcement ring is fixedly arranged on the side of the front disc outlet ring away from the rear disc body, and the trapezoidal grooves are evenly arranged on the side wall of the front disc outlet ring, and the trapezoidal grooves are staggered with the impeller outlet.

[0012] By adopting the above technical solution, the local strength of the weak link at the corner of the front disc is enhanced, and the trapezoidal grooves and the blade outlets are staggered to reduce excessive deformation at the impeller outlet.

[0013] Preferably, the number of the large auxiliary blades and the small auxiliary blades are the same, and the large auxiliary blades and the small auxiliary blades are arranged in the circumferential direction, the large auxiliary blades are close to the impeller outlet, and the small auxiliary blades are close to the hub body. The large auxiliary blades and the small auxiliary blades are both long and narrow, the length of the large auxiliary blades is 0.2-0.4 of the outer radius of the rear disk body, the width of the large auxiliary blades is 0.1-0.2 of the impeller outlet width, the length of the small auxiliary blades is 0.1-0.2 of the outer radius of the rear disk body, and the width of the small auxiliary blades is 0.05-0.1 of the impeller outlet width.

[0014] By adopting the above technical solution, the main shaft body drives the large and small auxiliary blades to rotate synchronously. The large and small auxiliary blades generate axial reaction force during the rotation process to offset the axial force generated by the operation of the impeller itself on the main shaft body. The small auxiliary blades generate negative pressure at the rear disc body close to the hub during the rotation process, thereby reducing the positive pressure at the gas seal seat and reducing the leakage of steam medium.

[0015] Preferably, an end cover is provided at one end of the hub body, the end cover is located at the impeller inlet, the other end of the hub body is the hub end face, the hub end face faces the gas seal seat, the side of the main shaft body facing the hub end face is the main shaft end face, and the distance between the hub end face and the main shaft end face is 5mm-20mm.

[0016] By adopting the above technical solution, by controlling the distance between the wheel hub end face and the spindle end face, it is determined whether the wheel hub body and the spindle body are installed in place.

[0017] Preferably, a tapered hole is formed on the outer ring wall of the hub body, a tapered surface is formed on the outer wall of the main shaft body, the outer diameter of the tapered surface is larger than the inner diameter of the tapered hole, the tapered hole and the tapered surface are interference connected, a spiral oil groove, a small annular groove and a large annular groove are formed on the tapered surface, the small annular groove is located on the side of the spiral oil groove away from the main shaft end face, the large annular groove is located on the side of the spiral oil groove close to the main shaft end face, one end of the spiral oil groove is interconnected with the small annular groove, and the other end of the spiral oil groove is interconnected with the large annular groove, an oil inlet hole is formed on one end of the main shaft body facing the end cover, a radial hole is formed in the main shaft body, one end of the radial hole is connected with the oil inlet hole, and the other end of the radial hole is connected with the small annular groove.

[0018] By adopting the above technical solution, the hydraulic oil is evenly distributed between the conical surface and the conical hole, so that the stress and deformation are even after the oil film is formed between the main shaft body and the hub body, and a radial distance is reserved for the advancement installation and pull-out disassembly of the main shaft body and the hub body, so as to facilitate the disassembly and assembly of the main shaft body and the hub body.

[0019] Preferably, a round nut, a stopping washer and a pressure plate are sleeved on the main shaft body, and the round nut, stopping washer and pressure plate are all located on the side of the conical surface away from the end face of the main shaft, the stopping washer is located between the round nut and the pressure plate, and the round nut and the pressure plate are both in contact with the stopping washer, the round nut is located on the side of the stopping washer away from the end face of the main shaft, the round nut is threadedly connected to the main shaft body, the pressure plate is located on the side of the stopping washer close to the conical surface, a sealing ring is arranged between the pressure plate and the wheel hub body, the stopping washer is provided with an inner card and an outer card, a stopping groove is opened on the main shaft body, the stopping groove is located on the side of the conical surface away from the end face of the main shaft, the width of the inner card is smaller than the width of the stopping groove, the inner card is clamped in the stopping groove, a clamping groove is opened on the round nut, the width of the outer card is smaller than the width of the clamping groove, and the outer card is clamped in the clamping groove.

[0020] By adopting the above technical solution, the stability of the connection between the hub body and the main shaft body is improved.

[0021] Preferably, a second sealing ring is arranged between the volute and the air seal seat, a sleeve is arranged between the air seal seat and the main shaft body, the air seal seat, the main shaft body and the sleeve are coaxially arranged, a sealing channel is arranged on the inner ring wall of the air seal seat, a sealing cavity is formed between the sealing channel and the outer wall of the sleeve, an inflation port, an air exhaust port and a drain port are arranged on the outer wall of the air seal seat, the inflation port, the air exhaust port and the drain port are all interconnected with the sealing channel, an air blocking ring is sleeved on the main shaft body, and the air blocking ring is located on the side of the air seal seat away from the hub body.

[0022] By adopting the above technical scheme, when the internal pressure of the volute is lower than the atmospheric pressure, clean steam with a pressure 10kPa-20kPa higher than the outlet pressure of the compression device is charged from the charging port, thereby reducing the situation where the atmosphere enters the compression device and affects the stability of the system; when the internal pressure of the volute is greater than the atmospheric pressure, the steam in the sealing chamber is led to the inlet pipe of the compression device or the non-condensable gas treatment tank through the exhaust port, thereby reducing the secondary steam leakage into the air to pollute the environment; when the steam leaks, the air retaining ring reduces the situation where the steam axially penetrates into the bearing seat and affects the safe operation of the bearing.

[0023] Preferably, a ring plate and a pressure ring are sleeved on the shaft sleeve, the ring plate is located between the wheel hub body and the air seal seat, the ring plate is fixedly connected to the shaft sleeve, one end of the pressure ring facing the wheel hub body and the end of the ring plate away from the wheel hub body abut against each other, the pressure ring is connected to the wheel hub body, and a sealing ring three is arranged between the wheel hub body and the pressure ring.

[0024] By adopting the above technical solution, the sealing ring three improves the air tightness of the equipment during operation.

[0025] In summary, the present application includes at least one of the following beneficial technical effects: 1. By setting the volute, main shaft body, hub body, front disc body, rear disc body, blades, gas seal seat, large auxiliary blades, small auxiliary blades and trapezoidal grooves, the failure rate of the impeller and the main shaft in coordinated operation is reduced, and the stability of the impeller and the main shaft in coordinated operation is improved; 2. By setting the front disc inlet ring, front disc connection ring, front disc outlet ring, front disc reinforcement ring and trapezoidal groove, the airflow can flow smoothly inside the impeller, the local strength of the weak link of the front disc body corner is enhanced, and the excessive deformation at the impeller outlet is reduced; 3. By arranging a tapered hole, a tapered surface, a spiral oil groove, a small annular groove, a large annular groove, an oil inlet hole and a radial hole, the main shaft body and the hub body can be easily disassembled and assembled. BRIEF DESCRIPTION OF THE DRAWINGS

[0026] Figure 1 It is a cross-sectional view of a fan structure for a small temperature rise centrifugal steam compression device in Example 1 of the present application.

[0027] Figure 2 It is a cross-sectional view showing the connection relationship between the hub body and the front disc body in Example 1 of the present application.

[0028] Figure 3 It is a schematic diagram showing the position relationship between the trapezoidal groove and the blade in Example 1 of the present application.

[0029] Figure 4 It is a schematic diagram showing the positional relationship between the small annular groove and the large annular groove in Example 1 of the present application.

[0030] Figure 5 It is a cross-sectional view showing the connection relationship between the hub body and the main shaft body in Example 1 of the present application.

[0031] Figure 6 It is a schematic diagram showing the positional relationship between the outer card and the inner card in Example 1 of the present application.

[0032] Figure 7 It is a cross-sectional view showing the connection relationship between the gas seal seat and the main shaft body in Example 1 of the present application.

[0033] Figure 8 It is a cross-sectional view of a fan structure for a small temperature rise centrifugal steam compression device in Example 2 of the present application.

[0034] Fig. 9 It is a cross-sectional view showing the connection relationship between the hub body and the front disc body in Example 2 of the present application.

[0035] Fig.10 It is a schematic diagram showing the position relationship between the trapezoidal groove and the blade in Example 2 of the present application.

[0036] Fig.11 It is a schematic diagram showing the positional relationship between the small annular groove and the large annular groove in Example 2 of the present application.

[0037] Fig.12 It is a cross-sectional view showing the connection relationship between the hub body and the main shaft body in Example 2 of the present application.

[0038] Fig.13 It is a schematic diagram showing the positional relationship between the outer card and the inner card in Example 2 of the present application.

[0039] Fig.14 It is a cross-sectional view showing the connection relationship between the air seal seat and the main shaft body in Example 2 of the present application.

[0040] Explanation of the reference numerals: 1, impeller assembly; 11, hub body; 11a; hub end face; 11b, end cover; 12, blades; 12a, impeller inlet; 12b, impeller outlet; 13, front disc body; 13a, front disc inlet ring; 13b, front disc connecting ring; 13c, front disc outlet ring; 13d, front disc reinforcement ring; 14, rear disc body; 14a, small auxiliary blade; 14b, large auxiliary blade; 15, cone disc; 16, triangular reinforcement rib; 17, trapezoidal groove; 18, tapered hole; 2, main shaft assembly; 21, main shaft body; 21a, stop groove; 21b, small annular groove; 21c, spiral oil Groove; 21d, large annular groove; 21e, oil inlet hole; 21f, radial hole; 21g, main shaft end face; 22, shaft sleeve; 22a, ring plate; 23, pressure ring; 24, air retaining ring; 25, pressure plate; 26, stop washer; 26a, inner card; 26b, outer card; 27, round nut; 27a, snap-on groove; 28, conical surface; 3, stator group; 31, volute; 32, air seal seat; 32a, inflation port; 32b, exhaust port; 32c, drain port; 32d, sealing channel; 32e, sealing chamber; 41, sealing ring one; 42, sealing ring two; 43, sealing ring three. DETAILED DESCRIPTION

[0041] The following is combined with Figure 1-14 This application is described in further detail.

[0042] Example 1 of the present application discloses a fan structure for a centrifugal steam compression device with a small temperature rise. Figures 1 to 7 , including an impeller assembly 1, a main shaft assembly 2 and a stator assembly 3. The impeller assembly 1 includes a hub body 11, a plurality of blades 12, a front disc body 13, a rear disc body 14, a cone disc 15 and a plurality of triangular reinforcing ribs 16; the main shaft assembly 2 includes a main shaft body 21, a sleeve 22, a pressure ring 23, an air retaining ring 24, a pressure plate 25, a stop washer 26 and a round nut 27; the stator assembly 3 includes a volute 31 and an air seal seat 32.

[0043] refer to Figures 1 to 3The hub body 11 is a forged cylindrical structure. An end cover 11b is installed at one end of the hub body 11. The end cover 11b is arranged close to the front disc body 13. The other end of the hub body 11 is a hub end face 11a. The hub end face 11a is arranged close to the rear disc body 14. The blades 12, the rear disc body 14, the triangular reinforcement ribs 16 and the cone disc 15 are all welded to the hub body 11. The hub body 11, the front disc body 13, the rear disc body 14 and the cone disc 15 are coaxially arranged. The front disc body 13, the rear disc body 14 and the cone disc 15 are all sleeved on the hub body 11. The blades 12 are a quasi-three-dimensional arc structure. The number of blades 12 is 12. The blades 12 are evenly distributed along the circumferential direction of the hub body 11. The hub body 11, the front disc body 13, the rear disc body 14 and the cone disc 15 are all welded to the blades 12. The number of triangular reinforcing ribs 16 is 4, and the triangular reinforcing ribs 16 are evenly distributed along the circumference of the hub body 11. The cone disk 15 is sleeved on the triangular reinforcing ribs 16, and the hub body 11, the rear disk body 14 and the cone disk 15 are welded to the triangular reinforcing ribs 16. The impeller assembly 1 adopts an advanced cavity geometry design, which ensures the efficient aerodynamic performance of the impeller assembly 1 while reducing the manufacturing cost of the impeller assembly 1.

[0044] refer to Figures 1 to 3 The front disc body 13 is a three-stage conical structure, and the front disc body 13 includes a front disc inlet ring 13a, a front disc connecting ring 13b and a front disc outlet ring 13c. One end of the front disc connecting ring 13b is welded to the front disc inlet ring 13a, and the other end of the front disc connecting ring 13b is welded to the front disc outlet ring 13c. The front disc inlet ring 13a is located on the side of the front disc outlet ring 13c away from the rear disc body 14. The front disc inlet ring 13a, the front disc connecting ring 13b and the front disc outlet ring 13c are all welded to the blades 12, and the front disc inlet ring 13a, the front disc connecting ring 13b and the front disc outlet ring 13c are all fitted with the blades 12. An impeller inlet 12a is formed between the blades 12, the front disc inlet ring 13a and the end cover 11b, and an impeller outlet 12b is formed between the blades 12, the front disc outlet ring 13c and the rear disc body 14. The front disc inlet ring 13a is curve-fitted with the impeller inlet 12a, and the front disc outlet ring 13c is curve-fitted with the impeller outlet 12b to ensure smooth flow of airflow inside the impeller. The thickness of the front disc inlet ring 13a is the same as the thickness of the front disc outlet ring 13c, and the thickness of the front disc inlet ring 13a and the thickness of the front disc outlet ring 13c are both smaller than the thickness of the front disc connecting ring 13b. The front disc reinforcing ring 13d is welded to the side of the front disc outlet ring 13c away from the rear disc body 14, and the trapezoidal grooves 17 are evenly opened on the side wall of the front disc outlet ring 13c, and the trapezoidal grooves 17 are staggered with the impeller outlet 12b.

[0045] refer to Figure 1 and Figure 2, the rear disc body 14 is a circular plate structure, and the outer diameter of the rear disc body 14 is the same as the outer diameter of the front disc outlet ring 13c. Four large auxiliary leaves 14b and four small auxiliary leaves 14a are installed on the side of the rear disc body 14 away from the blades 12. The number of large auxiliary leaves 14b and small auxiliary leaves 14a is the same, and the large auxiliary leaves 14b and small auxiliary leaves 14a are evenly arranged along the circumferential direction of the hub body 11. The large auxiliary leaves 14b are close to the impeller outlet 12b, and the small auxiliary leaves 14a are close to the hub body 11. The large auxiliary leaves 14b and the small auxiliary leaves 14a are both long strips. The length of the large auxiliary leaves 14b is 0.2 of the outer radius of the rear disc body 14, and the width of the large auxiliary leaves 14b is 0.1 of the width of the impeller outlet 12b; the length of the small auxiliary leaves 14a is 0.1 of the outer radius of the rear disc body 14, and the width of the small auxiliary leaves 14a is 0.05 of the width of the impeller outlet 12b.

[0046] Reference Figure 4 and Figure 5 The hub body 11 is sleeved on the spindle body 21, and the side of the spindle body 21 facing the hub end face 11a is the spindle end face 21g. The distance between the hub end face 11a and the spindle end face 21g is 5mm. By controlling the distance between the hub end face 11a and the spindle end face 21g, it is determined whether the hub body 11 and the spindle body 21 are installed in place.

[0047] refer to Figures 2 to 5 The inner ring wall of the hub body 11 is provided with a conical hole 18, and the outer wall of the spindle body 21 is provided with a conical surface 28. The outer diameter of the conical surface 28 is larger than the inner diameter of the conical hole 18, and the conical hole 18 is connected with the conical surface 28 by interference fit. The conical surface 28 is provided with a spiral oil groove 21c, a small annular groove 21b and a large annular groove 21d. The small annular groove 21b is located on the side of the spiral oil groove 21c away from the spindle end face 21g, and the large annular groove 21d is located on the side of the spiral oil groove 21c close to the spindle end face 21g. One end of the spiral oil groove 21c is connected to the small annular groove 21b, and the other end of the spiral oil groove 21c is connected to the large annular groove 21d. An oil inlet hole 21e is provided on one end of the spindle body 21 facing the end cover 11b, and a radial hole 21f is provided in the spindle body 21. One end of the radial hole 21f is connected to the oil inlet hole 21e, and the other end of the radial hole 21f is connected to the small annular groove 21b. The hydraulic oil is evenly distributed between the conical surface 28 and the conical hole 18, so that the stress and deformation are uniform after the oil film is formed between the main shaft body 21 and the hub body 11, and a radial distance is reserved for the advancement, installation, removal and disassembly of the main shaft body 21 and the hub body 11, so as to facilitate the disassembly and assembly of the main shaft body 21 and the hub body 11.

[0048] In order to improve the stability of the connection between the hub body 11 and the spindle body 21. Figures 4 to 6The round nut 27, the stop washer 26 and the pressure plate 25 are all sleeved on the main shaft body 21, and the round nut 27, the stop washer 26 and the pressure plate 25 are all located on the side of the conical surface 28 away from the main shaft end face 21g. The stop washer 26 is located between the round nut 27 and the pressure plate 25, and the round nut 27 and the pressure plate 25 are in contact with the stop washer 26. The round nut 27 is located on the side of the stop washer 26 away from the main shaft end face 21g, and the round nut 27 is threadedly connected to the main shaft body 21. The pressure plate 25 is located on the side of the stop washer 26 close to the conical surface 28, and an O-ring 41 is in contact between the pressure plate 25 and the hub body 11. An inner clamp 26a is provided on the inner ring of the stop washer 26, and a stop groove 21a is provided on the spindle body 21. The stop groove 21a is located on the side of the conical surface 28 away from the spindle end surface 21g. The width of the inner clamp 26a is smaller than the width of the stop groove 21a, and the inner clamp 26a is clamped in the stop groove 21a. An outer clamp 26b is installed on the outer ring of the stop washer 26, and a clamping groove 27a is provided on the round nut 27. The width of the outer clamp 26b is smaller than the width of the clamping groove 27a, and the outer clamp 26b is clamped in the clamping groove 27a.

[0049] Reference Figures 1 to 7 The shaft sleeve 22 and the air retainer 24 are both sleeved on the main shaft body 21, the shaft sleeve 22 is located between the air retainer 24 and the wheel hub body 11, and the air retainer 24 is arranged opposite to the wheel hub end face 11a. The shaft sleeve 22 is sleeved with a ring plate 22a, and the ring plate 22a and the shaft sleeve 22 are integrally formed. The pressure ring 23 is installed on the wheel hub end face 11a, and the wheel hub body 11 and the pressure ring 23 are abutted against an O-ring 43. The pressure ring 23 is sleeved on the shaft sleeve 22, and the end of the pressure ring 23 facing the wheel hub body 11 abuts against the end of the ring plate 22a away from the wheel hub body 11.

[0050] Reference Figures 1 to 7The volute 31 is mounted on the outside of the gas seal seat 32, and an O-ring 42 is abutted between the volute 31 and the gas seal seat 32. The gas seal seat 32 is sleeved on the shaft sleeve 22, one end of the gas seal seat 32 is opposite to the wheel hub end face 11a, and the other end of the gas seal seat 32 is opposite to the air retaining ring 24. A sealing channel 32d is provided on the inner ring wall of the gas seal seat 32, and a sealing cavity 32e is formed between the sealing channel 32d and the outer wall of the shaft sleeve 22. A labyrinth seal or a carbon ring seal is used in the sealing cavity 32e. An air filling port 32a, an air extraction port 32b and a water discharge port 32c are provided on the outer wall of the gas seal seat 32. The air filling port 32a, the air extraction port 32b and the water discharge port 32c are all connected to the sealing channel 32d. The air retaining ring 24 is sleeved on the main shaft body 21, and the air retaining ring 24 is located on the side of the gas seal seat 32 away from the wheel hub body 11. When the internal pressure of the volute 31 is lower than the atmospheric pressure, clean steam with a pressure 10kPa-20kPa greater than the outlet pressure of the compression device is charged from the charging port 32a, thereby reducing the situation where the atmosphere enters the compression device and affects the stability of the system. When the internal pressure of the volute 31 is greater than the atmospheric pressure, the steam in the sealed chamber 32e is introduced into the inlet pipe of the compression device or the non-condensable gas treatment tank through the exhaust port 32b, thereby reducing the situation where the secondary steam leaks into the air and pollutes the environment. When the steam leaks, the air retaining ring 24 reduces the situation where the steam axially enters the bearing seat and affects the safe operation of the bearing.

[0051] Example 2 of the present application discloses a fan structure for a centrifugal steam compression device with a small temperature rise. Figures 8 to 14 , including an impeller assembly 1, a main shaft assembly 2 and a stator assembly 3. The impeller assembly 1 includes a hub body 11, a plurality of blades 12, a front disc body 13, a rear disc body 14, a cone disc 15 and a plurality of triangular reinforcing ribs 16; the main shaft assembly 2 includes a main shaft body 21, a sleeve 22, a pressure ring 23, an air retaining ring 24, a pressure plate 25, a stop washer 26 and a round nut 27; the stator assembly 3 includes a volute 31 and an air seal seat 32.

[0052] refer to Figures 8 to 10The hub body 11 is a forged cylindrical structure. An end cover 11b is installed at one end of the hub body 11. The end cover 11b is arranged close to the front disc body 13. The other end of the hub body 11 is a hub end face 11a. The hub end face 11a is arranged close to the rear disc body 14. The blades 12, the rear disc body 14, the triangular reinforcement ribs 16 and the cone disc 15 are all welded to the hub body 11. The hub body 11, the front disc body 13, the rear disc body 14 and the cone disc 15 are coaxially arranged. The front disc body 13, the rear disc body 14 and the cone disc 15 are all sleeved on the hub body 11. The blades 12 are a quasi-three-dimensional arc structure. The number of blades 12 is 18. The blades 12 are evenly distributed along the circumferential direction of the hub body 11. The hub body 11, the front disc body 13, the rear disc body 14 and the cone disc 15 are all welded to the blades 12. The number of the triangular reinforcing ribs 16 is 8, and the triangular reinforcing ribs 16 are evenly distributed along the circumferential direction of the hub body 11. The cone disk 15 is sleeved on the triangular reinforcing ribs 16, and the hub body 11, the rear disk body 14 and the cone disk 15 are welded to the triangular reinforcing ribs 16. The impeller assembly 1 adopts an advanced cavity geometry design, which ensures the efficient aerodynamic performance of the impeller assembly 1 while reducing the manufacturing cost of the impeller assembly 1.

[0053] refer to Fig. 9 and Fig.10 The front disc body 13 is a three-stage conical structure, and the front disc body 13 includes a front disc inlet ring 13a, a front disc connecting ring 13b and a front disc outlet ring 13c. One end of the front disc connecting ring 13b is welded to the front disc inlet ring 13a, and the other end of the front disc connecting ring 13b is welded to the front disc outlet ring 13c. The front disc inlet ring 13a is located on the side of the front disc outlet ring 13c away from the rear disc body 14. The front disc inlet ring 13a, the front disc connecting ring 13b and the front disc outlet ring 13c are all welded to the blades 12, and the front disc inlet ring 13a, the front disc connecting ring 13b and the front disc outlet ring 13c are all fitted with the blades 12. An impeller inlet 12a is formed between the blades 12, the front disc inlet ring 13a and the end cover 11b, and an impeller outlet 12b is formed between the blades 12, the front disc outlet ring 13c and the rear disc body 14. The front disc inlet ring 13a is curve-fitted with the impeller inlet 12a, and the front disc outlet ring 13c is curve-fitted with the impeller outlet 12b to ensure smooth flow of airflow inside the impeller. The thickness of the front disc inlet ring 13a is the same as the thickness of the front disc outlet ring 13c, and the thickness of the front disc inlet ring 13a and the thickness of the front disc outlet ring 13c are both smaller than the thickness of the front disc connecting ring 13b. The front disc reinforcing ring 13d is welded to the side of the front disc outlet ring 13c away from the rear disc body 14, and the trapezoidal grooves 17 are evenly opened on the side wall of the front disc outlet ring 13c, and the trapezoidal grooves 17 are staggered with the impeller outlet 12b.

[0054] refer to Fig. 9, the rear disc body 14 is a circular plate structure, and the outer diameter of the rear disc body 14 is the same as the outer diameter of the front disc outlet ring 13c. Eight large auxiliary leaves 14b and eight small auxiliary leaves 14a are installed on the side of the rear disc body 14 away from the blades 12. The number of large auxiliary leaves 14b and small auxiliary leaves 14a is the same, and the large auxiliary leaves 14b and small auxiliary leaves 14a are evenly arranged along the circumferential direction of the hub body 11. The large auxiliary leaves 14b are close to the impeller outlet 12b, and the small auxiliary leaves 14a are close to the hub body 11. The large auxiliary leaves 14b and the small auxiliary leaves 14a are both long strips. The length of the large auxiliary leaves 14b is 0.4 of the outer radius of the rear disc body 14, and the width of the large auxiliary leaves 14b is 0.2 of the width of the impeller outlet 12b; the length of the small auxiliary leaves 14a is 0.2 of the outer radius of the rear disc body 14, and the width of the small auxiliary leaves 14a is 0.1 of the width of the impeller outlet 12b.

[0055] Reference Figures 9 to 12 The hub body 11 is sleeved on the spindle body 21, and the side of the spindle body 21 facing the hub end face 11a is the spindle end face 21g. The distance between the hub end face 11a and the spindle end face 21g is 20mm. By controlling the distance between the hub end face 11a and the spindle end face 21g, it is determined whether the hub body 11 and the spindle body 21 are installed in place.

[0056] refer to Figures 9 to 12 The inner ring wall of the hub body 11 is provided with a conical hole 18, and the outer wall of the spindle body 21 is provided with a conical surface 28. The outer diameter of the conical surface 28 is larger than the inner diameter of the conical hole 18, and the conical hole 18 is connected with the conical surface 28 by interference fit. The conical surface 28 is provided with a spiral oil groove 21c, a small annular groove 21b and a large annular groove 21d. The small annular groove 21b is located on the side of the spiral oil groove 21c away from the spindle end face 21g, and the large annular groove 21d is located on the side of the spiral oil groove 21c close to the spindle end face 21g. One end of the spiral oil groove 21c is connected to the small annular groove 21b, and the other end of the spiral oil groove 21c is connected to the large annular groove 21d. An oil inlet hole 21e is provided on one end of the spindle body 21 facing the end cover 11b, and a radial hole 21f is provided in the spindle body 21. One end of the radial hole 21f is connected to the oil inlet hole 21e, and the other end of the radial hole 21f is connected to the small annular groove 21b. The hydraulic oil is evenly distributed between the conical surface 28 and the conical hole 18, so that the stress and deformation are uniform after the oil film is formed between the main shaft body 21 and the hub body 11, and a radial distance is reserved for the advancement, installation, removal and disassembly of the main shaft body 21 and the hub body 11, so as to facilitate the disassembly and assembly of the main shaft body 21 and the hub body 11.

[0057] In order to improve the stability of the connection between the hub body 11 and the spindle body 21. Figures 11 to 13The round nut 27, the stop washer 26 and the pressure plate 25 are all sleeved on the main shaft body 21, and the round nut 27, the stop washer 26 and the pressure plate 25 are all located on the side of the conical surface 28 away from the main shaft end face 21g. The stop washer 26 is located between the round nut 27 and the pressure plate 25, and the round nut 27 and the pressure plate 25 are in contact with the stop washer 26. The round nut 27 is located on the side of the stop washer 26 away from the main shaft end face 21g, and the round nut 27 is threadedly connected to the main shaft body 21. The pressure plate 25 is located on the side of the stop washer 26 close to the conical surface 28, and an O-ring 41 is in contact between the pressure plate 25 and the hub body 11. An inner clamp 26a is provided on the inner ring of the stop washer 26, and a stop groove 21a is provided on the spindle body 21. The stop groove 21a is located on the side of the conical surface 28 away from the spindle end surface 21g. The width of the inner clamp 26a is smaller than the width of the stop groove 21a, and the inner clamp 26a is clamped in the stop groove 21a. An outer clamp 26b is installed on the outer ring of the stop washer 26, and a clamping groove 27a is provided on the round nut 27. The width of the outer clamp 26b is smaller than the width of the clamping groove 27a, and the outer clamp 26b is clamped in the clamping groove 27a.

[0058] Reference Figures 8 to 14 The shaft sleeve 22 and the air retainer 24 are both sleeved on the main shaft body 21, the shaft sleeve 22 is located between the air retainer 24 and the wheel hub body 11, and the air retainer 24 is arranged opposite to the wheel hub end face 11a. The shaft sleeve 22 is sleeved with a ring plate 22a, and the ring plate 22a and the shaft sleeve 22 are integrally formed. The pressure ring 23 is installed on the wheel hub end face 11a, and the wheel hub body 11 and the pressure ring 23 are abutted against an O-ring 43. The pressure ring 23 is sleeved on the shaft sleeve 22, and the end of the pressure ring 23 facing the wheel hub body 11 abuts against the end of the ring plate 22a away from the wheel hub body 11.

[0059] Reference Figures 8 to 14The volute 31 is mounted on the outside of the gas seal seat 32, and an O-ring 42 is abutted between the volute 31 and the gas seal seat 32. The gas seal seat 32 is sleeved on the shaft sleeve 22, one end of the gas seal seat 32 is opposite to the wheel hub end face 11a, and the other end of the gas seal seat 32 is opposite to the air retaining ring 24. A sealing channel 32d is provided on the inner ring wall of the gas seal seat 32, and a sealing cavity 32e is formed between the sealing channel 32d and the outer wall of the shaft sleeve 22. A labyrinth seal or a carbon ring seal is used in the sealing cavity 32e. An air filling port 32a, an air extraction port 32b and a water discharge port 32c are provided on the outer wall of the gas seal seat 32. The air filling port 32a, the air extraction port 32b and the water discharge port 32c are all connected to the sealing channel 32d. The air retaining ring 24 is sleeved on the main shaft body 21, and the air retaining ring 24 is located on the side of the gas seal seat 32 away from the wheel hub body 11. When the internal pressure of the volute 31 is lower than the atmospheric pressure, clean steam with a pressure 10kPa-20kPa greater than the outlet pressure of the compression device is charged from the charging port 32a, thereby reducing the situation where the atmosphere enters the compression device and affects the stability of the system. When the internal pressure of the volute 31 is greater than the atmospheric pressure, the steam in the sealed chamber 32e is introduced into the inlet pipe of the compression device or the non-condensable gas treatment tank through the exhaust port 32b, thereby reducing the situation where the secondary steam leaks into the air and pollutes the environment. When the steam leaks, the air retaining ring 24 reduces the situation where the steam axially enters the bearing seat and affects the safe operation of the bearing.

[0060] The implementation principle of the fan structure for a centrifugal steam compression device with a small temperature rise in the present application is as follows: after the hub body 11 and the main shaft body 21 are assembled by matching the conical surface 28 with the conical hole 18, the round nut 27, the pressure plate 25 and the stop washer 26 are mounted on the main shaft body 21. Then the hydraulic system injects hydraulic oil through the oil inlet hole 21e, and the oil penetrates between the conical surface 28 and the inner wall of the conical hole 18 through the radial hole 21f, so that an oil film is formed between the hub body 11 and the main shaft body 21, thereby leaving a radial distance for the push-in installation and pull-out removal of the hub body 11. After that, it is determined whether it is installed in place according to the distance between the hub end face 11a and the main shaft end face 21g. After the hub body 11 and the main shaft body 21 are installed in place, the round nut 27 is tightened, and the outer clamp 26b of the stop washer 26 is bent into the clamping groove 27a of the round nut 27. Finally, the glands and the pressure ring 23 on the two end faces of the hub are installed to fix the shaft sleeve 22. When the main shaft assembly 2 drives the impeller assembly 1, the large auxiliary blade 14b offsets the axial force generated by the operation of the blade 12, reducing the vibration of the main shaft body 21, and the small auxiliary blade 14a generates negative pressure at the hub body 11, reducing the positive pressure at the gas seal seat 32, thereby reducing the leakage of steam medium. At the same time, the front disc reinforcement ring 13d enhances the local strength of the weak link at the corner of the front disc body 13, and the trapezoidal groove 17 is staggered with the outlet of the blade 12 to reduce the excessive deformation at the impeller outlet 12b. Reduce the failure rate of the impeller and the main shaft in cooperation, and improve the stability of the impeller and the main shaft in cooperation.

[0061] The above are all preferred embodiments of the present application, and the protection scope of the present application is not limited thereto. Therefore, any equivalent changes made according to the structure, shape, and principle of the present application should be included in the protection scope of the present application.

Claims

1. A fan structure for a centrifugal steam compression device with a small temperature rise, comprising a volute (31), a main shaft (21) rotatably arranged in the volute (31), a hub body (11) sleeved on the main shaft (21), a front disc body (13) and a rear disc body (14) sleeved on the hub body (11), the main shaft body (21), the hub body (11), the front disc body (13) and the rear disc body (14) are coaxially arranged, and a plurality of blades (12) are welded between the front disc body (13), the rear disc body (14) and the hub body (11), characterized in that: An air seal seat (32) is arranged between the volute (31) and the main shaft body (21), and the air seal seat (32) is located on the side of the rear disc body (14) away from the front disc body (13). A plurality of large auxiliary leaves (14b) and a plurality of small auxiliary leaves (14a) are fixedly arranged on the side of the rear disc body (14) away from the blades (12), and the large auxiliary leaves (14b) are located on the side of the small auxiliary leaves (14a) away from the hub body (11). A plurality of trapezoidal grooves (17) are provided on the front disc body (13), and the number of the trapezoidal grooves (17) is consistent with the number of the blades (12).

2. The fan structure for a small temperature rise centrifugal steam compression device according to claim 1, characterized in that: The blades (12) are of a quasi-three-dimensional arc structure, and the blades (12) are evenly distributed along the circumferential direction. The rear disc body (14) is of a circular plate structure, and the outer diameter of the rear disc body (14) is the same as the outer diameter of the front disc body (13). The hub body (11) is of a forged cylindrical structure, and a plurality of triangular reinforcing ribs (16) are welded between the hub body (11) and the rear disc body (14). A cone disc (15) is sleeved on the triangular reinforcing ribs (16), and the hub body (11), the rear disc body (14) and the blades (12) are all welded to the cone disc (15).

3. The fan structure for a small temperature rise centrifugal steam compression device according to claim 2, characterized in that: The front disc body (13) comprises a front disc inlet ring (13a), a front disc connecting ring (13b) and a front disc outlet ring (13c); one end of the front disc connecting ring (13b) is welded to the front disc inlet ring (13a); the other end of the front disc connecting ring (13b) is welded to the front disc outlet ring (13c); the front disc inlet ring (13a) is located on the side of the front disc outlet ring (13c) away from the rear disc body (14); the front disc inlet ring (13a), the front disc connecting ring (13b) and the front disc outlet ring (13c) are welded to the front disc inlet ring (13a); The front disc ring (13b) and the front disc outlet ring (13c) are all welded to the blade (12); the front disc inlet ring (13a), the front disc connecting ring (13b) and the front disc outlet ring (13c) are all fitted to the blade (12); an impeller inlet (12a) is formed between the blade (12), the front disc inlet ring (13a) and the hub body (11); an impeller outlet (12b) is formed between the blade (12), the front disc outlet ring (13c) and the rear disc body (14).

4. The fan structure for a small temperature rise centrifugal steam compression device according to claim 3, characterized in that: The thickness of the front disc inlet ring (13a) is the same as the thickness of the front disc outlet ring (13c), and both the thickness of the front disc inlet ring (13a) and the thickness of the front disc outlet ring (13c) are smaller than the thickness of the front disc connecting ring (13b). A front disc reinforcing ring (13d) is fixedly arranged on the side of the front disc outlet ring (13c) away from the rear disc body (14). The trapezoidal grooves (17) are evenly arranged on the side wall of the front disc outlet ring (13c), and the trapezoidal grooves (17) are staggered with the impeller outlet (12b).

5. The fan structure for a small temperature rise centrifugal steam compression device according to claim 3, characterized in that: The large auxiliary blades (14b) and the small auxiliary blades (14a) are of the same number, and the large auxiliary blades (14b) and the small auxiliary blades (14a) are arranged in a circumferential direction. The large auxiliary blades (14b) are close to the impeller outlet (12b), and the small auxiliary blades (14a) are close to the hub body (11). The large auxiliary blades (14b) and the small auxiliary blades (14a) are both in a long strip shape. The length of the large auxiliary blades (14b) is 0.2-0.4 of the outer radius of the rear disc body (14), and the width of the large auxiliary blades (14b) is 0.1-0.2 of the width of the impeller outlet (12b). The length of the small auxiliary blades (14a) is 0.1-0.2 of the outer radius of the rear disc body (14), and the width of the small auxiliary blades (14a) is 0.05-0.1 of the width of the impeller outlet (12b).

6. The fan structure for a small temperature rise centrifugal steam compression device according to claim 3, characterized in that: An end cover (11b) is provided at one end of the hub body (11), and the end cover (11b) is located at the impeller inlet (12a). The other end of the hub body (11) is a hub end face (11a), and the hub end face (11a) faces the gas seal seat (32). The side of the main shaft body (21) facing the hub end face (11a) is a main shaft end face (21g), and the distance between the hub end face (11a) and the main shaft end face (21g) is 5mm-20mm.

7. The fan structure for a small temperature rise centrifugal steam compression device according to claim 6, characterized in that: The inner ring wall of the hub body (11) is provided with a conical hole (18), the outer wall of the spindle body (21) is provided with a conical surface (28), the outer diameter of the conical surface (28) is larger than the inner diameter of the conical hole (18), the conical hole (18) and the conical surface (28) are interference-connected, and the conical surface (28) is provided with a spiral oil groove (21c), a small ring groove (21b) and a large ring groove (21d), the small ring groove (21b) is located on the side of the spiral oil groove (21c) away from the spindle end face (21g), and the large ring groove (21d) is located on the side of the spiral oil groove (21c) away from the spindle end face (21g). The groove (21c) is close to one side of the main shaft end face (21g), one end of the spiral oil groove (21c) is communicated with the small annular groove (21b), and the other end of the spiral oil groove (21c) is communicated with the large annular groove (21d). An oil inlet hole (21e) is provided on one end of the main shaft body (21g) facing the end cover (11b), and a radial hole (21f) is provided in the main shaft body (21), one end of the radial hole (21f) is communicated with the oil inlet hole (21e), and the other end of the radial hole (21f) is communicated with the small annular groove (21b).

8. The fan structure for a small temperature rise centrifugal steam compression device according to claim 7, characterized in that: A round nut (27), a stop washer (26) and a pressure plate (25) are sleeved on the spindle body (21); the round nut (27), the stop washer (26) and the pressure plate (25) are all located on the side of the conical surface (28) away from the spindle end surface (21g); the stop washer (26) is located between the round nut (27) and the pressure plate (25); the round nut (27) and the pressure plate (25) are in contact with the stop washer (26); the round nut (27) is located on the side of the stop washer (26) away from the spindle end surface (21g); the round nut (27) is threadedly connected to the spindle body (21); the pressure plate (25) is located on the side of the stop washer (26) close to the conical surface (28); A sealing ring (41) is arranged between the pressure plate (25) and the hub body (11); an inner clamp (26a) and an outer clamp (26b) are arranged on the stop washer (26); a stop groove (21a) is arranged on the main shaft body (21); the stop groove (21a) is located on the side of the conical surface (28) away from the main shaft end surface (21g); the width of the inner clamp (26a) is smaller than the width of the stop groove (21a); ​​the inner clamp (26a) is clamped in the stop groove (21a); ​​a clamping groove (27a) is arranged on the round nut (27); the width of the outer clamp (26b) is smaller than the width of the clamping groove (27a); the outer clamp (26b) is clamped in the clamping groove (27a).

9. The fan structure for a small temperature rise centrifugal steam compression device according to claim 1, characterized in that: A sealing ring (42) is arranged between the volute (31) and the air seal seat (32), a shaft sleeve (22) is arranged between the air seal seat (32) and the main shaft body (21), the air seal seat (32), the main shaft body (21) and the shaft sleeve (22) are coaxially arranged, a sealing channel (32d) is arranged on the inner ring wall of the air seal seat (32), a sealing cavity (32e) is formed between the sealing channel (32d) and the outer wall of the shaft sleeve (22), an air filling port (32a), an air exhaust port (32b) and a water discharge port (32c) are arranged on the outer wall of the air seal seat (32), the air filling port (32a), the air exhaust port (32b) and the water discharge port (32c) are all interconnected with the sealing channel (32d), an air blocking ring (24) is sleeved on the main shaft body (21), and the air blocking ring (24) is located on the side of the air seal seat (32) away from the hub body (11).

10. The fan structure for a small temperature rise centrifugal steam compression device according to claim 9, characterized in that: A ring plate (22a) and a pressure ring (23) are sleeved on the shaft sleeve (22); the ring plate (22a) is located between the wheel hub body (11) and the gas seal seat (32); the ring plate (22a) is fixedly connected to the shaft sleeve (22); one end of the pressure ring (23) facing the wheel hub body (11) abuts against one end of the ring plate (22a) away from the wheel hub body (11); the pressure ring (23) is connected to the wheel hub body (11); and a sealing ring (43) is arranged between the wheel hub body (11) and the pressure ring (23).

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