Single-driven two-stage dry-type oil-free screw compressor

Abstract

The invention discloses a two-stage dry type oil-free screw compressor driven by a single machine. The two-stage dry type oil-free screw compressor comprises a compressor body and a cooler. The compressor body is fixed at the upper end of the cooler; the compressor body comprises a first-stage compression mechanism, a compression motor, a second-stage compression mechanism, a first-stage exhaust pipe and a second-stage exhaust pipe. The compression motor is located between the first-stage compression mechanism and the second-stage compression mechanism and synchronously drives the first-stage compression mechanism and the second-stage compression mechanism. The first-stage exhaust pipe is connected with the exhaust end of the first-stage compression mechanism and the air inlet end of the cooler; the second-stage exhaust pipe is connected with the air outlet end of the cooler and the air inlet end of the second-stage compression mechanism. The vertical space is utilized, and the occupied area is reduced.

Description

Technical Field

[0001] This invention relates to the field of screw compressors, and more particularly to a single-machine driven two-stage dry oil-free screw compressor. Background Technology

[0002] A screw compressor is a positive displacement rotary compressor that compresses gases through the rotation of two meshing helical rotors (male and female rotors) within a casing. A dry, oil-free screw compressor is a type of screw compressor where no oil is involved in the compression process, ensuring the purity of the output gas.

[0003] Screw compressors typically have multi-stage compression mechanisms, with coolers installed between these stages to improve compression efficiency, reduce energy consumption, and protect equipment. However, since the coolers and compressors are independent devices and are arranged separately, the entire compression system occupies a large area, increasing workspace costs. Furthermore, a long pipeline is required between the coolers and compressors as a gas guide pipe. During gas transport, frictional resistance in the pipeline can cause a pressure drop, which is detrimental to air compression and can also lead to gas temperature rise. Summary of the Invention

[0004] To overcome the shortcomings of the prior art, the present invention provides a single-machine driven two-stage dry oil-free screw compressor, which has the advantage of reducing the floor space required.

[0005] In order to achieve the above object, the present invention adopts the following technical solutions: A single-unit driven two-stage dry oil-free screw compressor includes a compressor body and a cooler; the compressor body is fixed to the upper end of the cooler; the compressor body includes a primary compression mechanism, a compression motor, a secondary compression mechanism, a primary exhaust pipe, and a secondary exhaust pipe; the compression motor is located between the primary compression mechanism and the secondary compression mechanism and synchronously drives the primary compression mechanism and the secondary compression mechanism; the primary exhaust pipe connects the exhaust end of the primary compression mechanism and the inlet end of the cooler; the secondary exhaust pipe connects the outlet end of the cooler and the inlet end of the secondary compression mechanism.

[0006] By adopting the above technical solution, the compressor body is fixed on the upper part of the cooler, completing the integration of the two. This utilizes vertical space and reduces the floor space. At the same time, since the compressor body is located above the cooler, the length of the primary and secondary exhaust pipes can be shortened, reducing the impact of the pipelines on the gas and facilitating gas compression. Furthermore, the compressor motor is located between the primary and secondary compression mechanisms, so that the exhaust end of the primary compression mechanism is as close as possible to the inlet end of the cooler, and the inlet end of the secondary compression mechanism is as close as possible to the outlet end of the cooler. This shortens the length of the primary and secondary exhaust pipes, reduces the impact of the pipelines on the gas, and facilitates gas compression. In addition, both primary and secondary compression are driven by the compressor motor, reducing the number of motors, lowering costs, and eliminating the need to coordinate multiple motors, thus reducing control complexity. Moreover, the overall structure of the compressor body is more compact.

[0007] Optionally, the outlet end of the primary compression mechanism is located on the side of its inlet end away from the compression motor; the inlet end of the secondary compression mechanism is located on the side of its outlet end away from the compression motor.

[0008] By adopting the above technical solution, the length of the primary and secondary exhaust pipes can be further shortened, reducing the impact of the pipes on the gas and facilitating gas compression. On the other hand, with the length of the primary and secondary exhaust pipes remaining unchanged, the length of the cooler can be increased, resulting in better cooling effect and thus reducing the initial temperature of the secondary compression and lower energy consumption.

[0009] Optionally, the primary compression mechanism includes a primary male rotor and a primary female rotor; the vertical line connecting the centers of the primary male rotor and the primary female rotor forms a 45-degree angle with the intake and exhaust directions of the primary compression mechanism, respectively; the secondary compression mechanism includes a secondary male rotor and a secondary female rotor; the vertical line connecting the centers of the secondary male rotor and the secondary female rotor forms a 45-degree angle with the intake and exhaust directions of the secondary compression mechanism, respectively.

[0010] By adopting the above technical solution, the exhaust end of the primary compression mechanism and the intake end of the secondary compression mechanism can be set on the side, eliminating the need to place the exhaust pipe between the compressor body and the cooler, which facilitates the subsequent installation of the exhaust pipe. In addition, the height of the compressor body is reduced, thereby reducing the risk of tipping over.

[0011] Optionally, the primary exhaust pipe and the secondary exhaust pipe are vertically arranged straight pipes.

[0012] By adopting the above technical solution, the primary exhaust pipe and the secondary exhaust pipe are vertically installed straight pipes, which reduces the friction caused by pipe bends and is beneficial to gas compression.

[0013] Optionally, the cooler is provided with a gas-liquid separation mechanism at its end; the gas-liquid separation mechanism includes a gas-liquid separation pipe and a gas-liquid separation component disposed in the gas-liquid separation pipe; the gas-liquid separation component includes a plurality of inclined blades evenly distributed circumferentially around the center line of the gas-liquid separation pipe; air passages are formed between adjacent inclined blades; the projection portions of adjacent inclined blades on the vertical plane of the gas-liquid separation pipe overlap.

[0014] By adopting the above technical solution, the gas temperature decreases after being cooled by the cooler, which will generate liquid. This results in liquid being mixed in with the gas. When the gas flows along the gas channel, it will come into contact with the inclined blades, causing the liquid mixed in the gas to be retained on the inclined blades, thus achieving gas-liquid separation. Since the projections of adjacent inclined blades on the vertical plane of the gas-liquid separation tube overlap, there will be no gap channel parallel to the axial direction of the gas-liquid separation tube between adjacent inclined blades. This ensures that the gas mixed with liquid will definitely come into contact with the inclined blades, thereby improving the efficiency of gas-liquid separation.

[0015] Optionally, the primary compression mechanism includes an axial force balancing assembly located at the end of the primary compression mechanism; the axial force balancing assembly provides magnetic force to balance the axial forces of the male rotor and / or female rotor of the primary compression mechanism.

[0016] By adopting the above technical solution, the primary compression mechanism compresses air as the male and female rotors rotate. The male and female rotors are subjected to axial forces from the end to the front, which can damage the bearings supporting the male and female rotors. At this time, the axial force balancing component provides magnetism to balance the axial forces on the male and / or female rotors of the primary compression mechanism. The male and female rotors work more stably, while reducing the possibility of damaging the bearings supporting the male and female rotors and improving their service life.

[0017] Optionally, the housing of the compressor motor is provided with a coaxially arranged annular motor cooling chamber; the top of the compressor motor is connected to a first coolant inlet pipe and the bottom is connected to a first coolant outlet pipe; the other end of the first coolant inlet pipe is connected to an external coolant supply device; the other end of the first coolant outlet pipe is connected to the cooling chamber of the cooler; and a first solenoid valve is provided on the first coolant outlet pipe.

[0018] By adopting the above technical solution, the first solenoid valve is opened, and the coolant supply equipment provides coolant. The coolant enters the motor cooling chamber along the first coolant inlet pipe, then flows from top to bottom along the motor cooling chamber, and then enters the cooler along the first coolant outlet pipe. Since the position where the coolant enters the motor cooling chamber is higher than the position where it flows out of the motor cooling chamber, no additional driving component is required. In addition, the temperature of the coolant flowing in from the outside is relatively low, so the cooling effect on the compressor motor is better. At the same time, the temperature of the coolant flowing out of the compressor motor is lower than the temperature of the coolant in the cooler. Thus, this part of the coolant can be used in the cooler without the need for circulation treatment.

[0019] Optionally, the inner circumferential surface of the motor cooling cavity is provided with a plurality of coaxially arranged annular first fins distributed along its axial direction.

[0020] By adopting the above technical solution, the presence of the first fin increases the contact area with the coolant and improves the heat exchange efficiency. In addition, the first fin is coaxially arranged with the motor cooling cavity, so it will not obstruct the flow of coolant.

[0021] Optionally, a cooling mechanism is provided between the compressor motor and the cooler; a coaxially arranged annular motor cooling chamber is provided inside the housing of the compressor motor; the cooling mechanism is used to drive the coolant in the cooler to flow through the motor cooling chamber.

[0022] By adopting the above technical solution, the cooling mechanism drives the coolant in the cooler to flow through the motor cooling chamber, thus using the coolant in the cooler to cool the compressor motor, eliminating the need for additional coolant supply equipment.

[0023] Optionally, the cooling mechanism drives the coolant to flow alternately in both directions along the axial direction of the motor cooling chamber.

[0024] By adopting the above technical solution, the temperature of the coolant entering the motor cooling chamber is lower than the temperature of the coolant leaving the motor cooling chamber. The cooling mechanism changes the flow direction of the coolant entering the motor cooling chamber, that is, the coolant flows alternately in the positive and negative directions along the axial direction. This allows both ends of the motor cooling chamber to have the opportunity to contact the coolant that just enters the motor cooling chamber, thereby improving the cooling uniformity and reducing the possibility of temperature concentration in one place. Attached Figure Description

[0025] Figure 1 This is a structural schematic diagram of Embodiment 1 of the present invention.

[0026] Figure 2 This is a structural schematic diagram of Embodiment 1 of the present invention.

[0027] Figure 3 This is a schematic diagram of the structure of the two-stage male rotor and female rotor of the present invention.

[0028] Figure 4 This is a front view structural schematic diagram of the first-stage compression mechanism side behind the hidden first-stage compression end cap of the present invention.

[0029] Figure 5 This is a top view of the structure of Embodiment 1 of the present invention.

[0030] Figure 6 The present invention Figure 5 A schematic diagram of the cross-section of AA.

[0031] Figure 7 This is a schematic diagram of the structure of the cooler end cover of the present invention.

[0032] Figure 8 This is a schematic diagram of the structure of the gas-liquid separation component of the present invention during an explosion.

[0033] Figure 9 The present invention Figure 6 A magnified schematic diagram of part B in the diagram.

[0034] Figure 10 This is a cross-sectional structural schematic diagram of the second embodiment of the present invention.

[0035] Figure 11 The present invention Figure 10 A magnified schematic diagram of part C.

[0036] Figure 12 This is a cross-sectional structural schematic diagram of the third embodiment of the present invention.

[0037] Figure 13 The present invention Figure 12 A magnified schematic diagram of part D.

[0038] Explanation of reference numerals in the attached figures: 10. First-stage compression mechanism; 101. First-stage air inlet; 102. First-stage exhaust port; 11. First-stage compression support frame; 12. First-stage compression seat; 13. First-stage compression end cover; 14. First-stage male rotor; 141. First-stage first driven gear; 142. First-stage second driving gear; 15. First-stage female rotor; 151. First-stage second driven gear; 16. Magnetic component mounting base; 17. Magnetic component; 20. Compression motor; 200. Motor cooling chamber; 201. First fin; 202. First cooling chamber; 203. Support spacer ring; 204. Second cooling chamber; 205. Intermediate connecting hole; 206. Second fin; 21. Distributor; 22. First coolant inlet pipe; 23. Upper outlet pipe; 24. First stage first drive gear; 25. Second stage first drive gear; 30. Secondary compression mechanism; 301. Secondary air inlet; 302. Secondary exhaust port; 31. Secondary compression support frame; 32. Secondary compressor; 33. Secondary compression end cover; 34. Secondary male rotor; 341. Secondary first driven gear; 342. Secondary second driving gear; 35. Secondary female rotor; 351. Secondary second driven gear; 40. Primary exhaust pipe; 50. Cooler; 51. Cooling shell; 510. Cooling chamber; 511. Air inlet; 52. Cooler end cover; 53. Cooler end cap; 531. End cap connecting plate; 532. Inner liner ring column; 5320. Radial perforation; 533. Abutment ring; 54. Cooling mechanism; 541. Side support plate; 542. Heat exchanger pipe; 543. Heat exchanger fin; 55. Gas-liquid separation mechanism; 551. Gas-liquid separation pipe; 552. Connecting fixing ring; 553. Gas-liquid separation assembly; 5531. Intermediate support rod; 5532. Radial connecting plate; 5533. Inclined blade; 56. Concentrated air cap; 561. Concentrated air cap flange; 562. Concentrated air cap body; 5620. Exhaust notch; 57. Lower liquid outlet pipe; 570. Connecting slot; 571. First solenoid valve; 60. Secondary exhaust pipe; 80. Cooling mechanism; 81. Horizontal drive component; 82. Intermediate coolant distribution component; 821. Intermediate distribution seat; 822. Piston plate; 823. Horizontal tie rod; 824. Drive plate; 83. Horizontal pipeline; 84. Third pipeline; 841. Third upper control solenoid valve; 842. Third lower control solenoid valve; 85. Fourth pipeline; 851. Fourth control solenoid valve; 86. Second pipeline; 861. Second upper control solenoid valve; 862. Second lower control solenoid valve; 87. First pipeline; 871. First control solenoid valve. Detailed Implementation

[0039] The following is combined with Figures 1-13 The present invention will be described in further detail below.

[0040] Example 1: A single-unit driven two-stage dry oil-free screw compressor is disclosed, with reference to... Figure 1 and Figure 2The system includes a compressor body and a cooler 50. The compressor body is fixed to the upper end of the cooler 50. The compressor body includes a primary compression mechanism 10, a compression motor 20, a secondary compression mechanism 30, a primary exhaust pipe 40, and a secondary exhaust pipe 60. The compression motor 20 is located between the primary compression mechanism 10 and the secondary compression mechanism 30 and drives the primary compression mechanism 10 and the secondary compression mechanism 30 synchronously. The primary exhaust pipe 40 connects the exhaust end of the primary compression mechanism 10 and the inlet end of the cooler 50. The secondary exhaust pipe 60 connects the outlet end of the cooler 50 and the inlet end of the secondary compression mechanism 30. During operation, gas enters from the inlet end of the primary compression mechanism 10, flows sequentially through the primary compression mechanism 10, the primary exhaust pipe 40, the cooler 50, the secondary exhaust pipe 60, and the secondary compression mechanism 30, and finally exits from the exhaust end of the secondary compression mechanism 30. During this process, the gas sequentially completes one compression, cooling, and secondary compression.

[0041] refer to Figure 1-Figure 3 The primary compression mechanism 10 includes a primary compression support frame 11, a primary compression seat 12, a primary compression end cap 13, a primary male rotor 14, and a primary female rotor 15. The primary compression support frame 11, the primary compression seat 12, and the primary compression end cap 13 are sequentially connected as a single unit by bolts. A compression chamber is provided inside the primary compression seat 12. The primary male rotor 14 and the primary female rotor 15 are arranged in parallel and horizontally penetrate the primary compression seat 12 and the primary compression support frame 11. The screw portions of the primary male rotor 14 and the primary female rotor 15 are located inside the compression chamber of the primary compression seat 12. A primary air intake is provided on the primary compression seat 12. The primary air intake port 101 and the primary exhaust port 102 are connected to the compression chamber of the primary compressor seat 12. The primary male rotor 14 and the primary female rotor 15 are rotatably connected to the primary compressor seat 12 and the primary compression support frame 11 via bearings. A primary second drive gear 142 is coaxially fixed to the end of the primary male rotor 14 away from the compressor motor 20. A primary second driven gear 151 is coaxially fixed to the end of the primary female rotor 15 away from the compressor motor 20. The primary second drive gear 142 and the primary second driven gear 151 mesh with each other and are located inside the primary compression end cover 13. The bottom of the primary compression support frame 11 is provided with support feet, and the support feet are connected to the cooler 50 by bolts.

[0042] refer to Figure 1-Figure 3The secondary compression mechanism 30 includes a secondary compression support frame 31, a secondary compression seat 32, a secondary compression end cap 33, a secondary male rotor 34, and a secondary female rotor 35. The secondary compression support frame 31, the secondary compression seat 32, and the secondary compression end cap 33 are sequentially connected as a single unit by bolts. A compression chamber is provided inside the secondary compression seat 32. The secondary male rotor 34 and the secondary female rotor 35 are arranged in parallel and horizontally penetrate the secondary compression seat 32 and the secondary compression support frame 31. The screw portions of the primary male rotor 14 and the primary female rotor 15 are located inside the compression chamber of the secondary compression seat 32. A secondary air intake is provided on the secondary compression seat 32. The secondary compressor has an intake port 301 and a secondary exhaust port 302; the secondary intake port 301 and the secondary exhaust port 302 are respectively connected to the compression chamber of the secondary compressor base 32; the secondary male rotor 34 and the secondary female rotor 35 are rotatably connected to the secondary compressor base 32 and the secondary compressor support frame 31 through bearings; the secondary male rotor 34 is coaxially fixed with a secondary second drive gear 342 at the end away from the compressor motor 20; the secondary female rotor 35 is coaxially fixed with a secondary second driven gear 351 at the end away from the compressor motor 20; the secondary second drive gear 342 and the secondary second driven gear 351 mesh with each other and are located inside the secondary compressor end cover 33. The secondary compressor support frame 31 is provided with support feet at the bottom and the support feet are connected to the cooler 50 by bolts.

[0043] refer to Figure 1 and Figure 2 To shorten the length of the primary exhaust pipe 40 and the secondary exhaust pipe 60, the outlet of the primary compression mechanism 10 is located on the side away from the compressor motor 20 from its inlet end, that is, the primary exhaust port 102 is located on the side away from the compressor motor 20 from the primary inlet port 101; the inlet of the secondary compression mechanism 30 is located on the side away from the compressor motor 20 from its outlet end, that is, the secondary inlet port 301 is located on the side away from the compressor motor 20 from the secondary exhaust port 302. In this way, while ensuring that the cooler 50 is as long as possible, the primary exhaust port 102 is closer to the inlet end of the cooler 50 and the secondary inlet port 301 is closer to the outlet end of the cooler 50, thereby shortening the length of the primary exhaust pipe 40 and the secondary exhaust pipe 60.

[0044] refer to Figure 3 The compressor motor 20 is a coaxial dual-input motor, and one end of its output shaft is coaxially fixed with a first-stage first driving gear 24, and the other end is coaxially fixed with a second-stage first driving gear 25; the other end of the first-stage male rotor 14 is coaxially fixed with a first-stage first driven gear 141; the first-stage first driven gear 141 meshes with the first-stage first driving gear 24; the other end of the second-stage male rotor 34 is coaxially fixed with a second-stage first driven gear 341; the second-stage first driven gear 341 meshes with the second-stage first driving gear 25.

[0045] refer to Figure 1 , Figure 2 and Figure 4 To facilitate the installation of the primary exhaust pipe 40 and the secondary exhaust pipe 60, the primary exhaust pipe 40 and the secondary exhaust pipe 60 are located on the side. The primary air intake 101 is located on the top of the primary compression base 12, and the primary exhaust port 102 is located on the side of the primary compression base 12. The vertical line connecting the centers of the rotation axes of the primary male rotor 14 and the primary female rotor 15 forms a 45-degree angle with the air intake and exhaust directions of the primary compression mechanism 10, respectively. The secondary air intake 301 is located on the side of the secondary compression base 32, and the secondary exhaust port 302 is located on the top of the secondary compression base 32. The secondary compression mechanism 30 includes a secondary male rotor 34 and a secondary female rotor 35. The vertical line connecting the centers of the rotation axes of the secondary male rotor 34 and the secondary female rotor 35 forms a 45-degree angle with the air intake and exhaust directions of the secondary compression mechanism 30, respectively. One end of the primary exhaust pipe 40 is connected to the primary exhaust port 102, and the other end is connected to the air inlet of the cooler 50. One end of the secondary exhaust pipe 60 is connected to the secondary air inlet 301, and the other end is connected to the air outlet of the cooler 50.

[0046] In other embodiments, the primary intake port 101 and the primary exhaust port 102 are in the same vertical direction, and the shafts of the primary male rotor 14 and the primary female rotor 15 are on the same horizontal plane; the secondary intake port 301 and the secondary exhaust port 302 are in the same vertical direction, and the shafts of the secondary male rotor 34 and the secondary female rotor 35 are on the same horizontal plane; thus, the primary exhaust pipe 40 and the secondary exhaust pipe 60 can be configured as vertically arranged straight pipes. Compared with the bent configuration of the primary exhaust pipe 40 and the secondary exhaust pipe 60 in Embodiment 1, this reduces the friction caused by pipe bending and is beneficial for gas compression. However, for ease of installation, the compressor body in this embodiment is positioned higher than that in Embodiment 1, which increases the risk of tipping over.

[0047] refer to Figure 6 The cooler 50 includes a cylindrical cooling shell 51 with openings at both ends, a cooler end cover 53, a cooler end shield 52, a cooling mechanism 54, and a gas-liquid separation mechanism 55. The cooler end cover 53 and the cooler end shield 52 are respectively fixed to both ends of the cooling shell 51 by bolts. The cooler end cover 53 is located on the side closer to the primary compression mechanism 10. The cooler end shield 52 is located on the side closer to the secondary compression mechanism 30. The end of the cooling shell 51 closer to the primary compression mechanism 10 forms an air intake chamber 511, and the end away from the primary compression mechanism 10 forms a cooling chamber 510. One end of the primary exhaust pipe 40 is fixed to the cooling shell 51 and communicates with the air intake chamber. The cooling mechanism 54 is disposed in the cooling chamber 510. An exhaust chamber is formed inside the cooler end shield 52. The gas-liquid separation mechanism 55 is disposed at the end of the cooling mechanism 54 and is located in the exhaust chamber.

[0048] refer to Figure 6The cooling mechanism 54 includes a pair of circular plate-shaped side support plates 541, several heat exchange fins 543 distributed along the axial direction of the cooling chamber 510, and several heat exchange pipes 542 evenly distributed around the central axis of the cooling chamber 510. All the heat exchange fins 543 are located between the pair of side support plates 541. The heat exchange pipes 542 pass through the pair of side support plates 541 and all the heat exchange fins 543 in sequence. To facilitate air intake, both ends of the heat exchange pipes 542 are flush with the mutually distant end faces of the pair of side support plates 541. During operation, the cooling chamber 510 between the pair of side support plates 541 is partially filled with coolant, and this coolant is circulated and dissipated through an external coolant circulation device.

[0049] refer to Figure 6 and Figure 7 To facilitate the installation of the cooling mechanism 54, the diameter of the intake chamber 511 is larger than the diameter of the cooling chamber 510, and a stepped groove is formed at the connection between the intake chamber 511 and the cooling chamber 510; the diameter of the side support plate 541 near the primary compression mechanism 10 is adapted to the size of the stepped groove, and the diameter of the side support plate 541 away from the primary compression mechanism 10 is adapted to the size of the cooling chamber 510. The cooler end cap 53 includes a circular plate-shaped end cap connecting plate 531, a coaxial annular cylindrical inner liner 532 formed on the end face of the end cap connecting plate 531, and a coaxial annular abutment ring 533 formed on the other end of the inner liner 532; the inner liner 532 has a pair of radially open radial through holes 5320 formed on it; after installation, the end cap connecting plate 531 closes the opening of the cooling housing 51, the inner liner 532 is located in the intake chamber 511 and the pair of radial through holes 5320 are directly opposite the exhaust end of the first-stage exhaust pipe 40, and the abutment ring 533 abuts against the side support plate 541 near the first-stage compression mechanism 10.

[0050] refer to Figure 6 and Figure 8 The gas-liquid separation mechanism 55 includes a gas-liquid separation pipe 551 and a gas-liquid separation component 553 disposed in the gas-liquid separation pipe 551; the gas-liquid separation pipe 551 includes a separation pipe flange and a cylindrical separation pipe body; one end of the cooler end cover 52 is formed with a flange connected to the cooling shell 51; when the gas-liquid separation pipe 551 is installed, the separation pipe body of the gas-liquid separation pipe 551 extends into the exhaust chamber of the cooler end cover 52, and the separation pipe flange is located outside the cooler end cover 52 and is fixed to the flange of the cooler end cover 52 by bolts.

[0051] refer to Figure 6 and Figure 8The gas-liquid separation assembly 553 includes a central support rod 5531 and several inclined blades 5533 fixed to one end of the central support rod 5531 near the cooling mechanism 54. The central support rod 5531 is coaxially arranged with the gas-liquid separation pipe 551. The inclined blades 5533 are evenly distributed along the circumference of the central support rod 5531. An air passage is formed between adjacent inclined blades 5533. The projections of adjacent inclined blades 5533 on the vertical plane of the gas-liquid separation pipe 551 partially overlap. For connection with the gas-liquid separation pipe 551, an annular connecting ring 552 is fixed to the end of the separation pipe body away from the separation pipe flange. Several radially arranged radial connecting plates 5532 are formed at the end of the central support rod 5531 away from the inclined blades 5533. The outer ends of the radial connecting plates 5532 are fixed to the inner circumferential surface of the connecting ring 552. To reduce wind resistance, the two ends of the central support rod 5531 are formed into conical sharp corners.

[0052] refer to Figure 6 and Figure 8 To improve gas concentration and increase the efficiency of subsequent secondary compression, a concentrator cap 56 is connected to the intake end of the secondary exhaust pipe 60. The concentrator cap 56 includes a concentrator cap flange 561 connected to the secondary exhaust pipe 60 and a concentrator cap body 562. The concentrator cap body 562 consists of a cylindrical concentrator cap body and a hemispherical shell fixed to one end away from the concentrator cap flange 561. An exhaust notch 5620 is formed on one side of the concentrator cap body 562, which is directly opposite the connecting fixing ring 552.

[0053] In other embodiments, reference is made to... Figure 6 and Figure 9 In order to balance the axial force applied by compressed air to the first-stage male rotor 14 and the first-stage female rotor 15 when the first-stage compression mechanism 10 is working, an axial force balancing component is provided inside the first-stage compression end cover 13. The axial force balancing component includes a magnetic component mounting base 16 and a magnetic component 17 fixed on the magnetic component mounting base 16. The magnetic component 17 can be an electromagnet. The magnetic force generated by the magnetic component 17 can act on the first-stage male rotor 14, or on the first-stage female rotor 15, or on both the first-stage male rotor 14 and the first-stage female rotor 15 at the same time.

[0054] Example 2: The difference between Example 2 and Example 1 is as follows: (Refer to...) Figure 10 and Figure 11 The compressor motor 20 has a coaxially arranged annular motor cooling chamber 200 inside its housing. To increase the strength of the motor cooling chamber 200, an annular support ring 203 is formed in the middle of the motor cooling chamber 200. The support ring 203 divides the motor cooling chamber 200 into a first cooling chamber 202 and a second cooling chamber 204 distributed along its axial direction.

[0055] To dissipate heat from the compressor motor 20, the top of the compressor motor 20 is connected to several first coolant inlet pipes 22, and the bottom is connected to several first coolant outlet pipes. The first coolant inlet pipes 22 are connected to either the first cooling chamber 202 or the second cooling chamber 204, and the first coolant outlet pipes are also connected to either the first cooling chamber 202 or the second cooling chamber 204. The other end of the first coolant inlet pipe 22 is connected to an external coolant supply device. To evenly distribute the coolant, a distributor 21 is installed between all the first coolant inlet pipes 22 and the external coolant supply device. After passing through the distributor 21, the coolant flows evenly into the first coolant inlet pipes 22, allowing the coolant to enter the first cooling chamber 202 and the second cooling chamber 204. The other end of the first coolant outlet pipe is connected to the cooling chamber 510 of the cooler 50. A first solenoid valve 571 is installed on the first coolant outlet pipe.

[0056] refer to Figure 10 and Figure 11 For ease of disassembly and assembly, the first coolant outlet pipe includes an upper outlet pipe 23 fixed to the compressor motor 20 and a lower outlet pipe 57 fixed to the cooler 50; a first solenoid valve 571 is installed on the lower outlet pipe 57, and the upper end of the lower outlet pipe 57 is formed with a connecting slot 570 for vertical insertion of the lower end of the upper outlet pipe 23; a sealing ring is provided between the lower outlet pipe 57 and the upper outlet pipe 23.

[0057] When the compressor motor 20 needs to dissipate heat, the first solenoid valve 571 opens, and then the external coolant supply equipment increases the coolant. The coolant passes through the first coolant inlet pipe 22, the motor cooling chamber 200 and the first coolant outlet pipe in sequence and enters the cooling chamber 510, thereby completing the heat dissipation of the compressor motor 20.

[0058] refer to Figure 10 and Figure 11 In order to improve the heat dissipation efficiency of the compressor motor 20, a number of coaxially arranged annular first fins 201 are provided on the inner circumferential surface of the motor cooling chamber 200.

[0059] Example 3: The difference between Example 3 and Example 1 is as follows: (Refer to...) Figure 12 and Figure 13 The compressor motor 20 has a coaxially arranged annular motor cooling chamber 200 inside its housing. To increase the strength of the motor cooling chamber 200, an annular support ring 203 is formed in the middle of the motor cooling chamber 200. The support ring 203 divides the motor cooling chamber 200 into a first cooling chamber 202 and a second cooling chamber 204 distributed along its axial direction. Several circumferentially evenly distributed intermediate connecting holes 205 are formed on the support ring 203. The first cooling chamber 202 and the second cooling chamber 204 are connected through the intermediate connecting holes 205.

[0060] refer to Figure 12 and Figure 13 A cooling mechanism 80 is provided between the compressor motor 20 and the cooler 50; the cooling mechanism 80 is used to drive the coolant in the cooler 50 to flow through the motor cooling chamber 200, thereby realizing the heat dissipation of the compressor motor 20.

[0061] refer to Figure 12 and Figure 13 The cooling mechanism 80 includes a coolant drive assembly, a first pipe 87, a second pipe 86, a third pipe 84, and a fourth pipe 85. The upper ends of the first pipe 87 and the second pipe 86 are both connected to the first cooling chamber 202, and the lower ends of the first pipe 87 and the second pipe 86 are both connected to the cooling chamber 510. The upper ends of the third pipe 84 and the fourth pipe 85 are both connected to the second cooling chamber 204, and the lower ends of the third pipe 84 and the fourth pipe 85 are both connected to the cooling chamber 510. A first control solenoid valve 871 is installed on the first pipe 87. A second upper control solenoid valve 861 and a second lower control solenoid valve 862 are installed on the second pipe 86. A third upper control solenoid valve 841 and a third lower control solenoid valve 842 are installed on the third pipe 84. A fourth control solenoid valve 851 is installed on the fourth pipe 85.

[0062] refer to Figure 12 and Figure 13 The coolant drive assembly includes a coolant intermediate distribution component 82 and a horizontal drive component 81. The coolant intermediate distribution component 82 includes an internally hollow cylindrical intermediate distribution seat 821 and a piston plate 822 that slides axially and seals along the inner cavity of the intermediate distribution seat 821. Two or four horizontal tie rods 823 are formed on the vertical end faces of both sides of the piston plate 822. The horizontal tie rods 823 horizontally penetrate and slide in a sealed manner on the vertical sidewall of the corresponding side of the intermediate distribution seat 821. A drive plate 824 is fixed to the end of the horizontal tie rod 823 away from the piston plate 822. The horizontal drive component 81 is fixed to the cooler 50. The moving component 81 is used to drive a pair of drive plates 824 to move horizontally synchronously. The horizontal drive component 81 can be a double-headed cylinder or other linear drive component. Horizontal pipes 83 are fixed to the centers of the two vertical side walls of the intermediate distribution seat 821. The horizontal pipes 83 communicate with the inner cavity of the intermediate distribution seat 821. The other end of one horizontal pipe 83 is connected to the third pipe 84, and the connection point is located between the third upper control solenoid valve 841 and the third lower control solenoid valve 842. The other end of the other horizontal pipe 83 is connected to the second pipe 86, and the connection point is located between the second upper control solenoid valve 861 and the second lower control solenoid valve 862. The third pipe 84 and the second pipe 86 are located between the fourth pipe 85 and the second pipe 86. The fourth pipe 85 is located at the end of the second cooling chamber 204 away from the first cooling chamber 202. The first pipe 87 is located at the end of the first cooling chamber 202 away from the second cooling chamber 204.

[0063] refer to Figure 12 and Figure 13 In order to improve the heat dissipation efficiency of the compressor motor 20, a number of circumferentially evenly distributed second fins 206 are provided on the inner circumferential surface of the motor cooling cavity 200; the second fins 206 are in the shape of thin plates and their length direction is parallel to the axial direction of the motor cooling cavity 200.

[0064] When working, refer to Figure 13 The third lower control solenoid valve 842, the second upper control solenoid valve 861, and the fourth control solenoid valve 851 are opened. The horizontal drive component 81 drives the piston plate 822 to move to the right. This allows the coolant in the inner cavity of the intermediate distribution seat 821 located on the right side of the piston plate 822 to flow into the cooler 50 along the right horizontal pipe 83, the upper part of the second pipe 86, the first cooling chamber 202, the intermediate connecting hole 205, the second cooling chamber 204, and the fourth pipe 85. Simultaneously, as the piston plate 822 moves to the right, the coolant in the cooler 50 enters the inner cavity of the intermediate distribution seat 821 located on the left side of the piston plate 822 along the lower part of the third pipe 84 and the left horizontal pipe 83. Then, the third lower control solenoid valve 842 is closed. Solenoid valve 842, second upper control solenoid valve 861, and fourth control solenoid valve 851 open second lower control solenoid valve 862, third upper control solenoid valve 841, and first control solenoid valve 871. Horizontal drive component 81 drives piston plate 822 to move to the left. In this way, the coolant in the inner cavity of the intermediate distribution seat 821 located on the left side of piston plate 822 flows into cooler 50 along the left horizontal pipe 83, the upper part of the third pipe 84, the second cooling chamber 204, the intermediate connecting hole 205, the first cooling chamber 202, and the first pipe 87. According to the above principle, the left and right movement of piston plate 822 completes the action of driving coolant to flow alternately forward and backward along the axial direction of motor cooling chamber 200. Since the temperature of the coolant entering the motor cooling chamber 200 is lower than that of the coolant leaving the motor cooling chamber 200, the flow direction of the coolant entering the motor cooling chamber 200 is changed, that is, the coolant flows alternately in the positive and negative directions along the axial direction. This allows both ends of the motor cooling chamber 200 to have the opportunity to contact the coolant that just entered the motor cooling chamber, thereby improving the cooling uniformity and reducing the possibility of temperature concentration in one place.

[0065] The above are all preferred embodiments of the present invention and are not intended to limit the scope of protection of the present invention. Therefore, all equivalent changes made in accordance with the structure, shape and principle of the present invention should be covered within the scope of protection of the present invention.

Claims

1. A single-unit driven two-stage dry oil-free screw compressor, comprising a compressor body and a cooler (50); characterized in that: The compressor body is fixed to the upper end of the cooler (50); the compressor body includes a primary compression mechanism (10), a compression motor (20), a secondary compression mechanism (30), a primary exhaust pipe (40), and a secondary exhaust pipe (60); the compression motor (20) is located between the primary compression mechanism (10) and the secondary compression mechanism (30) and drives the primary compression mechanism (10) and the secondary compression mechanism (30) synchronously; the primary exhaust pipe (40) connects the exhaust end of the primary compression mechanism (10) and the intake end of the cooler (50); the secondary exhaust pipe (60) connects the outlet end of the cooler (50) and the intake end of the secondary compression mechanism (30).

2. The single-unit driven two-stage dry oil-free screw compressor according to claim 1, characterized in that: The outlet of the primary compression mechanism (10) is located on the side of its inlet that is away from the compression motor (20); the inlet of the secondary compression mechanism (30) is located on the side of its outlet that is away from the compression motor (20).

3. A single-unit driven two-stage dry oil-free screw compressor according to claim 1, characterized in that: The first-stage compression mechanism (10) includes a first-stage male rotor (14) and a first-stage female rotor (15); the vertical line connecting the centers of the rotating shafts of the first-stage male rotor (14) and the first-stage female rotor (15) forms a 45-degree angle with the air intake direction and the air exhaust direction of the first-stage compression mechanism (10), respectively; the second-stage compression mechanism (30) includes a second-stage male rotor (34) and a second-stage female rotor (35); the vertical line connecting the centers of the rotating shafts of the second-stage male rotor (34) and the second-stage female rotor (35) forms a 45-degree angle with the air intake direction and the air exhaust direction of the second-stage compression mechanism (30), respectively.

4. A single-unit driven two-stage dry oil-free screw compressor according to claim 1, characterized in that: The primary exhaust pipe (40) and the secondary exhaust pipe (60) are vertically arranged straight pipes.

5. A single-unit driven two-stage dry oil-free screw compressor according to claim 1, characterized in that: The cooler (50) is provided with a gas-liquid separation mechanism (55) at its end; the gas-liquid separation mechanism (55) includes a gas-liquid separation pipe (551) and a gas-liquid separation component (553) disposed in the gas-liquid separation pipe (551); the gas-liquid separation component (553) includes a plurality of inclined blades (5533) evenly distributed circumferentially with the center line of the gas-liquid separation pipe (551) as the axis; an air passage is formed between adjacent inclined blades (5533); the projections of adjacent inclined blades (5533) on the vertical plane of the gas-liquid separation pipe (551) partially overlap.

6. A single-unit driven two-stage dry oil-free screw compressor according to claim 1, characterized in that: The primary compression mechanism (10) includes an axial force balancing assembly located at the end of the primary compression mechanism (10); the axial force balancing assembly provides magnetic force to balance the axial forces of the male rotor and / or female rotor of the primary compression mechanism (10).

7. A single-unit driven two-stage dry oil-free screw compressor according to claim 1, characterized in that: The compressor motor (20) has a coaxially arranged annular motor cooling chamber (200) inside its housing; the top of the compressor motor (20) is connected to a first coolant inlet pipe (22) and the bottom is connected to a first coolant outlet pipe; the other end of the first coolant inlet pipe (22) is connected to an external coolant supply device; the other end of the first coolant outlet pipe is connected to the cooling chamber (510) of the cooler (50); a first solenoid valve (571) is provided on the first coolant outlet pipe.

8. A single-unit driven two-stage dry oil-free screw compressor according to claim 7, characterized in that: The inner circumferential surface of the motor cooling cavity (200) is provided with a plurality of coaxially arranged annular first fins (201) distributed along its axial direction.

9. A single-unit driven two-stage dry oil-free screw compressor according to claim 1, characterized in that: A cooling mechanism (80) is provided between the compressor motor (20) and the cooler (50); a coaxially arranged annular motor cooling chamber (200) is provided inside the housing of the compressor motor (20); the cooling mechanism (80) is used to drive the coolant in the cooler (50) to flow through the motor cooling chamber (200).

10. A single-unit driven two-stage dry oil-free screw compressor according to claim 9, characterized in that: The cooling mechanism (80) drives the coolant to flow alternately in both directions along the axial direction of the motor cooling chamber (200).

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