Two-stage screw compressor with new structure

Abstract

A two-stage screw compressor of a new structure is characterized in that: the structure includes a cylinder body, a primary rotor part, a secondary rotor part, a transmission chamber and an interstage accommodating chamber are arranged in the cylinder body, the transmission chamber is located at the exhaust end of the primary rotor part and the intake end of the secondary rotor part, and the exhaust end of the primary rotor part and the intake end of the secondary rotor part are located at the same side end, the interstage accommodating chamber is located between the primary rotor part and the secondary rotor part, and a partition is arranged in the interstage accommodating chamber, and the interstage accommodating chamber is directly connected to the transmission chamber. It has the advantages of being able to effectively simplify the flow trajectory of the gas-liquid mixture, being able to simplify the oil circuit, being simple and compact in overall structure, and being able to reduce the processing and assembly process requirements of the compressor.

Description

Technical Field

[0001] The present application relates to the technical field of oil-injected screw compressors, and in particular to a two-stage screw compressor with a novel structure. Background Art

[0002] Screw compressors are commonly used equipment in industrial applications, generally including single-stage screw compressors, two-stage screw compressors and three-stage screw compressors. At present, in order to achieve better energy-saving effects, two-stage screw compressors are widely used in the market. The main structures of two-stage screw compressors can be divided into upper and lower vertical structures, left and right horizontal structures and other structures. Conventional upper and lower vertical two-stage screw compressors on the market generally have the exhaust chambers of the first and second stages on the same side, so that the flow trajectory of the gas-liquid mixture discharged from the first stage to the second stage is S-shaped; therefore, in order to meet the lubrication of the rotor, bearings, gears and other components, the compressor will design a complex oil circuit structure or external oil pipe.

[0003] In addition, in the existing upper and lower vertical two-stage screw compressor, the chambers where the male and female rotors are located and the gear transmission chamber (gear box) are each closed, so in order to lubricate the components in different chambers (primary chamber, secondary chamber and transmission chamber), multiple oil circuits and oil circuit structures need to be set, which further increases the complexity of the oil circuit structure. In addition, since the gear box and the first and second compression chambers are sealed separately, different sealing structures and sealing cover plates need to be set, which also increases the axial length of the overall compressor and makes the structure not compact.

[0004] Therefore, it can be seen from the structure of the above-mentioned two-stage screw compressor that the conventional screw compressor with an upper and lower vertical structure has great limitations in design. Due to the layout of this traditional structure, the flow trajectory of the gas-liquid mixture between the first-stage compression host and the second-stage compression host is long, and the corresponding oil circuit structure is also relatively complex, which places high requirements on the processing and assembly of the entire equipment. In addition, since the traditional above-mentioned structure requires different oil circuits to be set in different chambers, such as spraying oil into the first-stage compression chamber, it is necessary to consider discharging the oil in time, otherwise it will cause blockage of the entire equipment, cause difficulties in the operation of the equipment, and cause damage to the compressor. In order to overcome the above-mentioned shortcomings, an oil return device must be set, and the setting of the oil return device will inevitably increase the complexity of the structure. Summary of the invention

[0005] In view of the above-mentioned deficiencies in the prior art, the present application provides a two-stage screw compressor with a new structure that can effectively simplify the flow trajectory of the gas-liquid mixture, simplify the oil circuit, have a simple and compact overall structure, and reduce the processing and assembly process requirements of the compressor.

[0006] In order to solve the above technical problems, the technical solution adopted in the present application is: the structure includes a cylinder body, and a first-stage rotor part, a second-stage rotor part, a transmission chamber and an interstage accommodating chamber are arranged in the cylinder body, the transmission chamber is located at the exhaust end of the first-stage rotor part and the intake end of the second-stage rotor part, and the exhaust end of the first-stage rotor part and the intake end of the second-stage rotor part are located on the same side end, the interstage accommodating chamber is located between the first-stage rotor part and the second-stage rotor part, and a partition is arranged in the interstage accommodating chamber, and the interstage accommodating chamber is directly connected with the transmission chamber.

[0007] Preferably, the first-stage rotor portion includes a first-stage rotor meshing with each other, a first-stage exhaust seat, a row end bearing mounted thereon, and a first-stage transmission structure, and the first-stage transmission structure is located at the exhaust end of the first-stage rotor and is located in the transmission chamber; the second-stage rotor portion includes a second-stage rotor meshing with each other, a second-stage inlet end bearing, a second-stage exhaust seat, a row end bearing mounted thereon, and a second-stage transmission structure; the second-stage transmission structure is located at the inlet end of the second-stage rotor, the inlet end and the exhaust end of the first-stage rotor are located on the same side, and the second-stage transmission structure is located in the transmission chamber.

[0008] The above structure is adopted, by setting an interstage accommodating chamber between the first-stage rotor part and the second-stage rotor part, a partition is set in the interstage accommodating chamber, and it is interconnected with the first-stage rotor part, the second-stage rotor part and the transmission chamber, and at the same time, the exhaust end of the first-stage rotor part and the air inlet end of the second-stage rotor part are set on the same side, both are located in the transmission chamber, and the exhaust seat of the second-stage rotor part is set in the direction of the side opposite to the second-stage transmission structure; such a setting changes the flow trajectory of the traditional gas-liquid mixture: the exhaust of the traditional first-stage rotor part and the air inlet of the two-stage rotor part are located on opposite sides, and the gas-liquid mixture comes out from one end of the first-stage exhaust chamber and goes to the other end to enter the second-stage air inlet, and then flows to the first-stage exhaust chamber. The gas is discharged from the two exhaust ends on the same side, forming an S-shaped flow trajectory, which causes a complex flow trajectory and is not conducive to full utilization of energy. In addition, the traditional structure is to set a sealing partition structure between the transmission chamber and the first and second rotor parts, and operate independently. In this way, different oil circuits need to be set at the rotor parts corresponding to the first and second stages to realize lubrication and oil spraying in the two chambers, and the transmission chamber is also disconnected from the first and second parts and isolated, and an oil injection oil circuit also needs to be set, which causes a complex oil circuit design. After adopting the compressor of the above structure of the present application, the flow trajectory of the gas-liquid mixture discharged from the first stage is that the exhaust end of the first rotor part enters the transmission chamber under the guidance of the inter-stage accommodating chamber and the partition, and then When entering the secondary air intake position at the same end, a C-shaped flow trajectory is presented. Such a flow trajectory can lubricate the transmission components (main shaft, gears and other components in the transmission chamber) and some bearings (first-stage and second-stage rotor bearings) respectively during the circulation process. The first-stage and second-stage rotor parts and the transmission chamber are interconnected, and there is no need to actively force oil supply and return to the transmission components (first-stage gear, second-stage gear, driving gear), nor is there a need to set up multiple oil circuits, which effectively simplifies the structure of the oil circuit; and the present application directly connects the chamber where the first-stage rotor part and the second-stage rotor part are located with the transmission chamber, and there is nothing between the two except the necessary intake and exhaust structures and bearings, shafts and transmission gears. There is no need to set up a sealing baffle, and it is a completely open setting, which can facilitate the oil-gas mixture coming out of the first-stage exhaust end to enter the transmission chamber more completely and smoothly, lubricate and cool the transmission parts, and then enter the second-stage intake position set on the same side. There is no active forced oil supply and oil return to the transmission parts (first-stage gear, second-stage gear, driving gear), no active forced oil supply and oil return to the bearings at the second-stage intake end, no active forced oil return to the bearings at the first-stage exhaust end, and no active forced oil supply to the first bearing on the main drive shaft; it effectively simplifies the oil circuit structure, shortens the flow trajectory of the oil-gas mixture, reduces energy consumption, and can make full use of the lubrication effect of the oil-gas mixture on each chamber.

[0009] Preferably, a main shaft bearing mounting seat is arranged on the end of the partition close to the transmission chamber, the partition extends to the outer wall of the main shaft bearing mounting seat, and the inner end face of the main shaft bearing mounting seat (the end face away from the transmission chamber) is connected to the partition; by adopting the above structure, the extension structure of the partition located at the position of the main shaft bearing mounting seat is limited, and the extension length of the partition located at the outer wall position of the main shaft bearing mounting seat is greater than the extension length of the inner end face partition of the main shaft bearing mounting seat, that is, the partition is located at the outer side of the main shaft bearing mounting seat and extends to overlap with the outer wall of the main shaft bearing mounting seat, while the inner end face position of the main shaft bearing mounting seat is not extended, but directly stops at the inner end face position to provide sufficient space for the installation of the main shaft gear, and at the same time, the outer extension length can guide the oil-gas mixture coming out of the exhaust end of the first-stage rotor part into the transmission chamber to lubricate the transmission parts first, and then enter the intake end position of the second-stage rotor part, thereby preventing the partition from being too short, causing a small amount or insufficient amount of oil-gas mixture to enter the transmission chamber and cause insufficient lubrication.

[0010] Further preferably, the main shaft bearing mounting seat is divided into an upper main shaft bearing mounting seat and a lower main shaft bearing mounting seat by a partition, and the main shaft bearing mounting seat is axially provided with a through hole, and the inner diameter of the through hole is greater than the thickness of the partition; by adopting the above-mentioned structure, the main shaft bearing mounting seat is fixed on the end face of the partition, and the connection area with the partition is as large as possible, so that the main shaft can be effectively supported to ensure the stability of the main shaft operation; in addition, the through hole can guide the oil-gas mixture to enter the transmission chamber through the through hole of the upper main shaft bearing mounting seat, and then enter the secondary rotor part through the through hole of the lower main shaft bearing mounting seat, so as to realize a large flow of the oil-gas mixture in a completely C-shaped trajectory, prevent oil accumulation on the partition, and effectively improve the lubrication effect on the transmission structure in the transmission chamber.

[0011] Preferably, the primary transmission structure is installed on one of the primary rotors, and the secondary transmission structure is installed on one of the secondary rotors; the above structure can provide more stable power to the rotors in the primary and secondary rotor parts, ensuring the effective compression of the air by the rotors, and at the same time can achieve effective communication between the primary and secondary rotors and the transmission chamber, and achieve smoother flow of the oil-gas mixture, thereby achieving lubrication of the transmission components and forming a C-shaped flow trajectory.

[0012] Preferably, the partition has a first inclined surface, and the first inclined surface is gradually inclined downward on the upper surface of the partition from the end away from the transmission chamber to the end close to the transmission chamber; with the above structure, the first inclined surface can play a drainage role for the gas-liquid mixture in the first-stage compression chamber, so that the gas-liquid mixture flows out from the exhaust chamber end of the first-stage rotor and enters the transmission chamber to realize oil supply and lubrication of the transmission components, and then enters the air intake end of the second-stage compression chamber, thereby realizing the diversion of the gas-liquid mixture and effectively preventing the accumulation of oil in the channel from affecting the normal operation of the compressor, and can ensure that the oil in the chamber will not accumulate on the partition, but will directly enter the transmission chamber to realize the lubrication of the transmission components, and will be mixed again under the action of the transmission components and enter the second-stage compression chamber.

[0013] Further preferably, the partition is also provided with a second inclined surface, and the second inclined surface is gradually inclined downward from both sides of the partition width direction to the middle on the upper surface of the partition; with the above structure, the setting of the second inclined surface can concentrate and enrich the gas-liquid mixture from both sides of the partition or the inter-stage accommodating chamber in the width direction toward the middle direction, and combined with the first inclined surface structure, it is convenient for the gas-liquid mixture to enter the transmission chamber and the secondary compression chamber more completely, thereby realizing the diversion of the gas-liquid mixture and the lubrication of components, and can also effectively prevent the accumulation of oil and gas in the upper chamber and cause damage to the entire compressor.

[0014] Further preferably, a first chamfer is provided on the end face of the partition close to the transmission chamber end (the first chamfer here includes the partition end face connected to the inner end face of the main shaft bearing mounting seat and the partition end face extending to the outer side wall of the main shaft bearing mounting seat), and the first chamfer extends downward in an arc from the upper surface of the cylinder stage partition to the end face; that is, an arc-shaped chamfer structure is provided on the partition at the tail end position where the gas-liquid mixture flows to the transmission chamber, and the chamfer structure extends downward in an arc from the upper surface of the partition to the end face, so that the gas-liquid mixture can easily enter the transmission chamber when it flows to this place, and backflow is not likely to occur even in the motor vibration state.

[0015] Further preferably, a second chamfer is provided at the connection between the partition and the inner wall of the cylinder body, and the second chamfer extends downward in an arc shape from the inner wall of the cylinder body to the upper surface of the partition; that is, an arc-shaped chamfer structure is also formed at the connection between the partition and the inner wall of the cylinder body, and the arc is opposite to the arc-shaped convex direction of the first chamfer. Such an arc-shaped chamfer structure can ensure that the gas-liquid mixture is gathered toward the middle of the partition, and then smoothly and completely enters the transmission chamber along the inclination direction of the first inclination angle, and oil backflow is not likely to occur even when the motor is vibrating.

[0016] Further preferably, the partition, the main shaft bearing mounting seat and the secondary inlet bearing mounting seat are all connected with reinforcing ribs; the setting of this structure not only has the function of strengthening the structure, but also can provide a firm support for the operation of the transmission components, while also ensuring the circulation of oil and gas, and effectively lubricating the bearings and gears.

[0017] Preferably, the first-stage exhaust seat and the cylinder body are integrally formed; that is, the present application has a structure in which the first-stage exhaust seat and the cylinder body are integrally formed, that is, the cylinder and the first-stage exhaust seat are an integrally formed structure, and the two are not independent components, and do not require a connecting structure with each other, but can be an integral structure cast in one piece using a casting or other process. Because if the first-stage exhaust seat is installed on the cylinder by screws and locating pins, due to the particularly high requirements for the processing (concentricity, verticality, position) and assembly of the rotor mounting holes, if the processing requirements are not met, the rotor installed on the cylinder will be slightly misaligned, affecting the energy efficiency of the machine, and even serious accidents such as scraping the cylinder may occur; in addition, because the first-stage exhaust seat needs to be installed inside the cylinder, the forced oil supply structure of the first-stage exhaust end bearing needs to be relatively complex in design, and the use of the above-mentioned structure in which the first-stage exhaust seat and the cylinder body are integrally formed can effectively avoid the above-mentioned deficiencies.

[0018] Preferably, a main shaft bearing is arranged on the main shaft bearing mounting seat, a main shaft is arranged in the main shaft bearing, a main shaft transmission component (gear) is arranged on the main shaft, the first-level transmission structure includes a first-level bearing arranged on the first-level exhaust seat, a first-level transmission shaft (i.e., an output shaft in the first-level rotor) is arranged in the first-level bearing, and a first-level transmission component (gear) is arranged on the first-level transmission shaft, the second-level transmission structure includes a second-level bearing arranged on the second-level inlet bearing mounting seat, a second-level transmission shaft (i.e., an output shaft in the second-level rotor) is arranged in the second-level bearing, and a second-level transmission component (gear) is arranged on the second-level transmission shaft; the main shaft transmission component is respectively connected to the first-level transmission component and the second-level transmission component; with the above structure, the main shaft is connected to the driving mechanism, which can effectively realize the power output of the main shaft transmission component to the first and second rotors, and provide a stable power source for the operation of the first and second rotors. BRIEF DESCRIPTION OF THE DRAWINGS

[0019] Figure 1 This is a cross-sectional structural diagram of a two-stage screw compressor of a novel structure of the present application.

[0020] Figure 2 This is a schematic diagram of the three-dimensional structure of the two-stage screw compressor cylinder of the present application (Example 1).

[0021] Figure 3 for Figure 2 Schematic diagram of the structure of the main view.

[0022] Figure 4 for Figure 2 Schematic diagram of the axonometric cross-sectional view of the structure.

[0023] Figure 5 A schematic diagram of the three-dimensional structure of the cylinder of the two-stage screw compressor of this application (Example 2)

[0024] Figure 6 for Figure 2 A structural schematic diagram of a cross-sectional view corresponding to a first-stage compression chamber in a two-stage screw compressor cylinder (a removable first-stage exhaust seat is provided at the first-stage exhaust seat mounting position).

[0025] Figure 7 for Figure 5 A structural schematic diagram of a cross-sectional view corresponding to a first-stage compression chamber in a two-stage screw compressor cylinder (an integrally formed first-stage exhaust seat is provided at the first-stage exhaust seat mounting position).

[0026] As shown in the figure: a. Cylinder body, 1.1. First-stage rotor, 1.2. First-stage exhaust seat, 1.3. First-stage bearing, 1.4. First-stage transmission shaft, 1.5. First-stage transmission component, 2. Second-stage rotor, 2.1. Second-stage rotor, 2.2. Second-stage exhaust seat, 3. Transmission chamber, 4. Partition, 4.1. First inclined surface, 4.2. Second inclined surface, 4.3. First chamfer, 4.4. Second chamfer, 5. Main shaft bearing mounting seat, 5.1. Upper half main shaft bearing mounting seat, 5.2. Lower half main shaft bearing mounting seat, 5.3. Through hole, 5.4. Main shaft bearing, 5.5. Main shaft, 5.6. Main shaft transmission component, 6. Second-stage inlet bearing mounting seat, 6.1. Secondary bearing, 6.2. Secondary transmission shaft, 6.3. Secondary transmission component, 7. Reinforcement rib, 8. End cover. DETAILED DESCRIPTION

[0027] The following will clearly and completely describe the technical solutions in the embodiments of the present application in conjunction with the drawings in the embodiments. Obviously, the described embodiments are only preferred embodiments, not all embodiments. Based on the embodiments in the present application, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the present invention;

[0028] It should also be noted that when a component is referred to as being "fixed to" another component, it may be directly on the other component or there may also be another intermediate component, fixed through the intermediate component. When a component is considered to be "connected" to another component, it may be directly connected to the other component or there may be another intermediate component at the same time. When a component is considered to be "set on" another component, it may be directly set on the other component or there may be another intermediate component at the same time. The terms "vertical", "horizontal", "left", "right" and similar expressions used herein are for illustrative purposes only. Unless otherwise defined, all technical and scientific terms used herein have the same meaning as those generally understood by technicians in the technical field of the present invention. The terms used in the specification of the present invention herein are only for the purpose of describing specific embodiments and are not intended to limit the present invention. The term "and / or" used herein includes any and all combinations of one or more related listed items.

[0029] Example 1

[0030] As attached Figure 1 As shown, a two-stage screw compressor of a novel structure of the present application is shown, and the structure includes a cylinder body a, wherein the cylinder body a is provided with a primary rotor portion 1, a secondary rotor portion 2, a transmission chamber 3 (a transmission structure is provided in the transmission chamber, such as a primary and secondary transmission structure, and a main shaft transmission structure, etc.) and an interstage accommodating chamber, wherein the transmission chamber 3 is located at the exhaust end of the primary rotor portion 1 and the intake end of the secondary rotor portion 2, and the exhaust end of the primary rotor portion 1 and the intake end of the secondary rotor portion 2 are located at the same side end (i.e., the same direction end, both are the right side ends as shown in the figure), the interstage accommodating chamber is located between the primary rotor portion 1 and the secondary rotor portion 2, and a partition is provided in the interstage accommodating chamber. Plate 4, the interstage accommodating cavity is directly connected to the transmission chamber 3; the first-stage rotor part 1 includes a first-stage rotor 1.1 that is meshed with each other, a first-stage exhaust seat 1.2 and a row end bearing and a first-stage transmission structure installed thereon, and the first-stage transmission structure is located at the exhaust end of the first-stage rotor 1.1 and is located in the transmission chamber 3; the second-stage rotor part 2 includes a second-stage rotor 2.1 that is meshed with each other, a second-stage inlet end bearing, a second-stage exhaust seat 2.2 and a row end bearing and a second-stage transmission structure installed thereon; the second-stage transmission structure is located at the inlet end of the second-stage rotor 2.2, and the inlet end is located on the same side as the exhaust end of the first-stage rotor, and the second-stage transmission structure is located in the transmission chamber 3.

[0031] The above structure is adopted, by setting an interstage accommodating chamber between the first-stage rotor part and the second-stage rotor part, a partition is set in the interstage accommodating chamber, and it is interconnected with the first-stage rotor part, the second-stage rotor part and the transmission chamber, and at the same time, the exhaust end of the first-stage rotor part and the air inlet end of the second-stage rotor part are set on the same side, both are located in the transmission chamber, and the exhaust seat of the second-stage rotor part is set in the direction of the side opposite to the second-stage transmission structure; such a setting changes the flow trajectory of the traditional gas-liquid mixture: the exhaust of the traditional first-stage rotor part and the air inlet of the two-stage rotor part are located on opposite sides, and the gas-liquid mixture comes out from one end of the first-stage exhaust chamber and goes to the other end to enter the second-stage air inlet, and then flows to the first-stage exhaust chamber. The gas is discharged from the two exhaust ends on the same side, forming an S-shaped flow trajectory, which causes a complex flow trajectory and is not conducive to full utilization of energy. In addition, the traditional structure is to set a sealing partition structure between the transmission chamber and the first and second rotor parts, and operate independently. In this way, different oil circuits need to be set at the rotor parts corresponding to the first and second stages to realize lubrication and oil spraying in the two chambers, and the transmission chamber is also disconnected from the first and second parts and isolated, and an oil injection oil circuit also needs to be set, which causes a complex oil circuit design. After adopting the compressor of the above structure of the present application, the flow trajectory of the gas-liquid mixture discharged from the first stage is that the exhaust end of the first rotor part enters the transmission chamber under the guidance of the inter-stage accommodating chamber and the partition, and then When entering the secondary air intake position at the same end, a C-shaped flow trajectory is presented. Such a flow trajectory can lubricate the transmission components (main shaft, gears and other components in the transmission chamber) and some bearings (first-stage and second-stage rotor bearings) respectively during the circulation process. The first-stage and second-stage rotor parts and the transmission chamber are interconnected, and there is no need to actively force oil supply and return to the transmission components (first-stage gear, second-stage gear, driving gear), nor is there a need to set up multiple oil circuits, which effectively simplifies the structure of the oil circuit; and the present application directly connects the chamber where the first-stage rotor part and the second-stage rotor part are located with the transmission chamber, and there is nothing between the two except the necessary intake and exhaust structures and bearings, shafts and transmission gears. There is no need to set up a sealing baffle, and it is a completely open setting, which can facilitate the oil-gas mixture coming out of the first-stage exhaust end to enter the transmission chamber more completely and smoothly, lubricate and cool the transmission parts, and then enter the second-stage intake position set on the same side. There is no active forced oil supply and oil return to the transmission parts (first-stage gear, second-stage gear, driving gear), no active forced oil supply and oil return to the bearings at the second-stage intake end, no active forced oil return to the bearings at the first-stage exhaust end, and no active forced oil supply to the first bearing on the main drive shaft; it effectively simplifies the oil circuit structure, shortens the flow trajectory of the oil-gas mixture, reduces energy consumption, and can make full use of the lubrication effect of the oil-gas mixture on each chamber.

[0032] As attached Figure 1-4As shown, the partition 4 described in the present application is provided with a spindle bearing mounting seat 5 on the end close to the transmission chamber, and the partition 4 extends to the outer wall of the spindle bearing mounting seat 5, and the inner end face of the spindle bearing mounting seat 5 (the end face away from the transmission chamber) is connected to the partition 4; by adopting the above structure, the extension structure of the partition located at the position of the spindle bearing mounting seat is limited, and the extension length of the partition located at the outer wall position of the spindle bearing mounting seat is greater than the extension length of the inner end face partition of the spindle bearing mounting seat, that is, the partition is located at the outer side of the spindle bearing mounting seat and extends to overlap with the outer wall of the spindle bearing mounting seat, while the inner end face position of the spindle bearing mounting seat is not extended, and directly stops at the inner end face position to provide sufficient space for the gear installation of the main shaft, and at the same time, the outer extension length can guide the oil-gas mixture coming out of the exhaust end of the first-stage rotor part into the transmission chamber to lubricate the transmission parts first, and then enter the intake end position of the second-stage rotor part, thereby preventing the partition from being too short, causing a small amount or insufficient amount of oil-gas mixture to enter the transmission chamber and cause insufficient lubrication.

[0033] As attached Figure 2-3 As shown, the spindle bearing mounting seat 5 described in the present application is divided into an upper half spindle bearing mounting seat 5.1 and a lower half spindle bearing mounting seat 5.2 by a partition, and the spindle bearing mounting seat 5 is axially provided with a through hole 5.3, and the inner diameter of the through hole 5.3 is greater than the thickness of the partition (in addition, from the attached Figure 2 , 3 As can be seen from Figure 5, a circle of mounting holes is set on the wall thickness of the spindle bearing mounting seat near the through hole. This mounting hole is a countersunk hole rather than a through hole. It is used to install a small spring for pre-tightening the bearing, which will not be described here); the specific upper half spindle bearing mounting seat 5.1 is larger than the lower half spindle bearing mounting seat 5.2. With the above structure, the spindle bearing mounting seat is fixed on the end face of the partition, and the connection area with the partition is as large as possible (the end face and the outer wall are connected to form a three-sided connection method), which can effectively support the spindle and ensure the stability of the spindle operation; in addition, the spindle bearing mounting seat is axially provided with a plurality of holes. The structure is in the form of a through hole, and the thickness of the partition is smaller than the inner diameter of the through hole, so that a gap is formed between the bearing mounting seat and the partition, and the oil-gas mixture can be guided by the partition and the through hole into the transmission chamber, and then into the secondary rotor part. Since the specific transmission chamber of the present application is directly connected with the inter-stage accommodating chamber, it is not necessary to spray oil in each chamber separately. Instead, after spraying oil in the chamber of the first-stage rotor part by relying on the specific structure, the common lubrication of each chamber can be achieved. The above-mentioned structure can ensure a large flow rate of oil injection, which completely enters the lower main shaft bearing mounting hole from the upper main shaft bearing mounting hole, thereby preventing the injection oil from accumulating on the partition.

[0034] As attached Figure 2-3As shown, as a preferred embodiment of the present application, the secondary rotor part 2 described in the present application is provided with a secondary inlet end bearing mounting seat 6 near the inlet end, and the secondary inlet end bearing mounting seat 6 is located directly below the main shaft bearing mounting seat 5 (directly below here is a preferred embodiment, which is not reflected in the claims to avoid limiting the scope of protection), and in this embodiment, the upper and lower positions of the secondary inlet end bearing mounting seat 6 and the main shaft bearing mounting seat 5 are aligned and are on the same vertical straight line, thereby providing effective and stable guarantees for the entire transmission; with this structure, the oil-gas mixture coming out of the exhaust end of the first-stage rotor part can first pass through the transmission chamber and then enter the secondary rotor part, realizing a C-shaped flow trajectory, and also ensuring the stability of the transmission device operation; of course, the above-mentioned secondary inlet end bearing mounting seat 6 and the main shaft bearing mounting seat 5 of the present application can also be not aligned in the upper and lower positions, and the vertical position can be adjusted according to the specific working conditions.

[0035] As attached Figure 1 As shown, the primary transmission structure described in the present application is installed on one of the primary rotors 1.1 (exit shaft), and the installation position is located at the exhaust end of the primary rotor and in the transmission chamber 3. The primary inlet end sealing cover and the inlet end bearing structure installed thereon are on the other side of the transmission chamber; the secondary transmission structure is installed on one of the secondary rotors 2.1 (exit shaft), and the installation position is located at the inlet end of the secondary rotor. The inlet end and the exhaust end of the primary rotor are located on the same side, and the secondary transmission structure is located in the transmission chamber 3 (the secondary inlet end bearing structure is on the same side as the inter-stage transmission structure); adopt the above The above structure can provide more stable power to the rotors in the first and second rotor parts, ensure the effective compression of the rotors, and at the same time realize the effective connection between the first and second rotors and the transmission chamber, realize the smoother flow of the oil-gas mixture, realize the lubrication of the transmission parts and the formation of a C-shaped flow trajectory; and the above structure of the present application is equivalent to designing the exhaust chamber of the first-stage rotor (the space for installing the exhaust seat) inside the transmission chamber, so that the oil-gas mixture coming out of the first-stage exhaust seat can be used to lubricate the gears and bearings in the transmission chamber, and the independent oil supply structure of the partial transmission chamber and the second-stage transmission chamber can be eliminated.

[0036] As attached Figure 1As shown, the spindle bearing mounting seat 5 described in the present application is provided with a spindle bearing 5.4, a spindle 5.5 is arranged in the spindle bearing 5.4 (the other end of the spindle is connected to the driving mechanism to drive the spindle to operate), and a spindle transmission component (gear) 5.6 is arranged on the spindle; the primary transmission structure includes a primary bearing 1.3 arranged on the primary exhaust seat 1.2, a primary transmission shaft 1.4 is arranged in the primary bearing 1.3 (that is, it can directly be an output shaft in the primary rotor), a primary transmission component (gear) 1.5 is arranged on the primary transmission shaft, and the secondary transmission structure includes a primary bearing 1.3 arranged on the secondary inlet A secondary bearing 6.1 on the end bearing mounting seat 6, a secondary transmission shaft 6.2 (that is, it can directly be an output shaft of the secondary rotor) is arranged in the secondary bearing 6.1, and a secondary transmission component (gear) 6.3 is arranged on the secondary transmission shaft 6.2; the main shaft transmission component 5.3 is respectively connected to the primary transmission component 1.5 and the secondary transmission component 6.3 (the gears are meshed with each other to realize the operation of the compressor); with the above structure, the other end of the main shaft is connected to the driving mechanism, which can effectively realize the power output of the main shaft transmission component to the primary and secondary rotors, and provide a stable power source for the operation of the primary and secondary rotors.

[0037] As attached Figure 4 As shown, the partition 4 described in the present application has a first inclined surface 4.1, and the first inclined surface 4.1 is gradually inclined downward from the end away from the transmission chamber to the end close to the transmission chamber on the upper surface of the partition 4, that is, Figure 4 Direction, the upper surface of the partition is inclined from high to low from left to right; with the above structure, the first inclined surface can play a drainage role for the gas-liquid mixture in the first-stage compression chamber, so that the gas-liquid mixture flows out from the exhaust chamber end of the first-stage rotor, enters the transmission chamber to realize the oil supply and lubrication of the transmission components, and then enters the air inlet end of the second-stage compression chamber, thereby realizing the diversion of the gas-liquid mixture and effectively preventing the accumulation of oil in the channel from affecting the normal operation of the compressor, which can ensure that the oil in the chamber will not accumulate on the partition, but will directly enter the transmission chamber to realize the lubrication of the transmission components, and will be mixed again under the action of the transmission components and enter the second-stage compression chamber.

[0038] As attached Figure 3 As shown, the partition 4 described in the present application is also provided with a second inclined surface 4.2, and the second inclined surface 4.2 is formed on the upper surface of the partition 4 and gradually tilts downward from both sides to the middle in the direction of the partition width. Figure 3In the direction, that is, the left and right sides are inclined downward toward the middle direction to form a structure with high sides and concave in the middle; with the above structure, the setting of the second inclined surface can concentrate and enrich the gas-liquid mixture from the two sides of the partition or the inter-stage accommodating chamber in the width direction toward the middle direction, and combined with the first inclined surface structure, it is convenient for the gas-liquid mixture to enter the transmission chamber and the secondary compression chamber more completely, realizing the guidance of the gas-liquid mixture and the lubrication of the components, and can also effectively prevent the accumulation of oil and gas in the upper chamber and cause damage to the entire compressor.

[0039] A preferred embodiment of the present application is to simultaneously set a first inclined surface and a second inclined surface on the partition. Of course, selecting one of the two settings also has the same effect of improving the fluidity of the oil in the cylinder.

[0040] As attached Figure 4 As shown, the partition 4 described in the present application is provided with a first chamfer 4.3 on the end face close to the transmission chamber end (the chamfer here includes the partition end face connected to the inner end face of the main shaft bearing mounting seat, that is, the partition end face at the corresponding position of the bearing mounting seat through hole and the partition end face extending to the outer wall of the main shaft bearing mounting seat); that is, an arc-shaped chamfer structure is provided on the partition at the tail end position where the gas-liquid mixture flows to the transmission chamber, and the chamfer structure extends downward in an arc from the upper surface of the partition to the end face (the arc of the first chamfer bulges upward), so that the gas-liquid mixture can flow to this place and enter the transmission chamber conveniently and smoothly, especially the oil will no longer be retained or accumulated on the partition, and backflow is not likely to occur even when the motor is in a vibrating state.

[0041] As attached Figure 1-3 As shown, a second chamfer 4.4 is provided at the connection between the partition 4 described in the present application and the inner wall of the cylinder body a, and the second chamfer 4.4 extends downward in an arc shape from the inner wall of the cylinder body a to the upper surface of the partition 3; that is, an arc-shaped chamfer structure is also formed at the connection between the cylinder-stage partition plate and the inner wall of the cylinder body, and the arc is opposite to the arc-shaped convex direction of the first chamfer, and the arc of the chamfer is convex downward. Such an arc-shaped chamfer structure can ensure that the gas-liquid mixture is gathered toward the middle of the partition along the second inclined surface, and then smoothly and completely enters the transmission chamber along the inclined direction of the first inclined surface, and oil backflow is not likely to occur even when the motor is vibrating.

[0042] A preferred embodiment of the present application is to set a first chamfer and a second chamfer on the partition at the same time. Of course, selecting one of the two settings will also have the same effect of improving the fluidity of the oil in the cylinder.

[0043] As attached Figure 2-3As shown, the partition 4, the main shaft bearing mounting seat 5 and the secondary input end bearing mounting seat 6 described in the present application are all connected with reinforcing ribs 7, and a plurality of reinforcing ribs 7 are provided, and the plurality of reinforcing ribs can form a mesh support structure; the setting of this structure not only has the function of strengthening the structure, but also can provide a firm support for the operation of the transmission components, and at the same time can ensure the sufficient circulation of oil and gas, and effectively lubricate the bearings and gears.

[0044] As attached Figure 1 , 6 As shown, the first-stage exhaust seat 1.2 of the present application and the cylinder body a are connected in a detachable manner. Figure 1 It can be seen that an installation position and a mounting hole for installing a first-stage exhaust seat are set at the exhaust end of the first-stage rotor part. The first-stage exhaust seat 1.2 and the cylinder body a are separate components, which are connected by a connecting device, such as bolt connection, screw connection, etc.

[0045] As attached Figure 1 , 2 As shown in Figure 5, the exhaust end of the first-stage rotor part 1 (the end where the first-stage exhaust seat is located), the intake end of the second-stage rotor part 2 (located on the same side below the first-stage exhaust seat) and the transmission chamber 3 of the present application are directly connected, and no sealing partition is required between them. The right end is the end cover 8 of the transmission chamber. Such connected chambers constitute an inter-stage accommodating chamber, which provides an effective flow path for the circulation of the oil-gas mixture. The transmission chamber of this embodiment can be regarded as a part of the inter-stage accommodating chamber.

[0046] Example 2

[0047] As attached Figure 5 , 7 As shown, the compressor structure of the embodiment of the present application is basically the same as that described in Example 1, the difference is that in the preferred embodiment of the present application, the first-stage exhaust seat 1.2 is integrally formed with the cylinder body a; that is, the present application sets the first-stage exhaust seat and the cylinder body as an integrally formed structure, that is, the cylinder and the first-stage exhaust seat are an integrally formed structure, and the two are not independent components, and do not require a connecting structure with each other, but can be an integral structural member cast in one piece by a casting or other process. Because if the first-stage exhaust seat is installed on the cylinder by screws or locating pins, etc., due to the particularly high requirements for the processing (concentricity, verticality, position) and assembly of the rotor mounting hole, if the processing requirements are not met, the rotor installed on the cylinder will be slightly misaligned, affecting the energy efficiency of the machine, and even serious accidents such as scraping the cylinder may occur; in addition, because the first-stage exhaust seat needs to be installed inside the cylinder, the forced oil supply structure of the first-stage row end bearing needs to be designed to be relatively complex, and the use of the above-mentioned structure in which the first-stage exhaust seat and the cylinder body are integrally formed can effectively avoid the above-mentioned shortcomings.

[0048] The interstage accommodating chamber of the present application may include a transmission chamber, and the two may also be combined to be referred to as an interstage / transmission chamber. The interstage / transmission chamber of the present application is composed of a space formed by a first and second rotor part, a cylinder, an end cover, i.e., a gear box cover and a main transmission part thereon, a second transmission part, a partition, etc.; the exhaust part of the first rotor part, the first exhaust seat and its bearing structure are on the same side as the interstage transmission structure (i.e., the transmission structure in the transmission chamber); the inlet sealing cover of the first rotor part and the inlet bearing structure installed thereon are on the other side of the transmission chamber; the first transmission structure is directly installed on one of the rotors (the output shaft), and the installation position is the rotor Exhaust end; the secondary inlet bearing structure of the present application is on the same side as the interstage transmission structure; the secondary transmission structure of the present application is directly installed on one of the rotors (the output shaft), and the installation position is the intake end of the rotor; the exhaust and transmission parts of the first-stage rotor part of the present application are installed on the interstage side, and the intake and transmission parts of the second-stage transmission part are installed on the interstage side; the above-mentioned arrangement satisfies the change of the flow trajectory of the oil-gas mixture in the cylinder body from the traditional S-type to the C-type, simplifies the trajectory, improves energy utilization, and can also simplify the oil circuit structure to ensure the lubrication of the first and second rotor parts and the transmission structure and the sufficient flow of the first-stage oil-gas mixture.

[0049] The specific structure of the novel double-stage screw compressor of the present application is shown in the attached Figure 1 As shown, the first-stage rotor part described in the present application is located at the upper part of the cylinder body, the second-stage rotor part is located at the lower part of the cylinder body, the transmission chamber is located at the exhaust end of the first-stage rotor part, the interstage accommodating chamber is located between the first-stage compression chamber and the second-stage compression chamber, and extends along the axial direction of the first-stage compression chamber and the second-stage compression chamber to communicate with the transmission chamber, the first-stage exhaust seat, the intake end of the second-stage rotor part and the transmission chamber are all located on the same side end of the interstage accommodating chamber; such a structure does not require a traditional isolation end cover between the gear box and the first and second main engines, and can realize the flow of the oil-gas mixture inside the entire cylinder body, and the second-stage rotor part is closer to the transmission chamber (gear box) and the structure is more compact, which is conducive to the installation of the subsequent three-stage compression main engine, leaving more assembly space for the three stages, and the structure is also more compact.

Claims

1. A two-stage screw compressor with a new structure, characterized in that: The structure includes a cylinder body, wherein a primary rotor part, a secondary rotor part, a transmission chamber and an interstage accommodating chamber are arranged in the cylinder body, wherein the transmission chamber is located at the exhaust end of the primary rotor part and the intake end of the secondary rotor part, and the exhaust end of the primary rotor part and the intake end of the secondary rotor part are located at the same side end, wherein the interstage accommodating chamber is located between the primary rotor part and the secondary rotor part, and a partition is arranged in the interstage accommodating chamber, and wherein the interstage accommodating chamber is directly connected with the transmission chamber; A spindle bearing mounting seat is arranged on the end of the partition close to the transmission chamber, the partition extends to the outer side wall of the spindle bearing mounting seat, and the inner end surface of the spindle bearing mounting seat is connected to the partition; The spindle bearing mounting seat is divided into an upper spindle bearing mounting seat and a lower spindle bearing mounting seat by a partition, and the upper spindle bearing mounting seat is larger than the lower spindle bearing mounting seat; The partition plate has a first inclined surface, and the first inclined surface is formed by gradually inclining downward from the end away from the transmission chamber to the end close to the transmission chamber on the upper surface of the partition plate; The partition is provided with a second inclined surface, and the second inclined surface is formed by gradually inclining downward from both sides to the middle of the partition in the direction of the partition width on the upper surface of the partition; A first chamfer is provided on the end surface of the partition close to the transmission chamber end, and the first chamfer extends downward in an arc shape from the upper surface of the partition to the end surface; A second chamfer is provided at the connection between the partition and the inner wall of the cylinder body, and the second chamfer extends downward in an arc shape from the inner wall of the cylinder body to the upper surface of the partition.

2. The two-stage screw compressor according to claim 1, characterized in that: The first-stage rotor part includes a first-stage rotor meshing with each other, a first-stage exhaust seat and an exhaust end bearing mounted thereon, and a first-stage transmission structure, wherein the first-stage transmission structure is located at the exhaust end of the first-stage rotor and in the transmission chamber; The secondary rotor part includes a secondary rotor that is meshed with each other, a secondary inlet end bearing, a secondary exhaust seat and an exhaust end bearing and a secondary transmission structure installed thereon; the secondary transmission structure is located at the inlet end of the secondary rotor, the inlet end and the exhaust end of the primary rotor part are located on the same side, and the secondary transmission structure is located in the transmission chamber.

3. The two-stage screw compressor according to claim 1, characterized in that: The spindle bearing mounting seat is axially provided with a through hole, and the inner diameter of the through hole is greater than the thickness of the partition plate.

4. The two-stage screw compressor according to claim 2, characterized in that: The primary transmission structure is installed on one of the primary rotors, and the secondary transmission structure is installed on one of the secondary rotors.

5. The two-stage screw compressor according to claim 4, characterized in that: The partition plate, the main shaft bearing mounting seat and the secondary inlet end bearing mounting seat are all connected with reinforcing ribs.

6. The two-stage screw compressor according to claim 4, characterized in that: The first-stage exhaust seat and the cylinder body are integrally formed.

7. The two-stage screw compressor according to claim 4, characterized in that: A main shaft bearing is arranged on the main shaft bearing mounting seat, a main shaft is arranged in the main shaft bearing, and a main shaft transmission component is arranged on the main shaft; the primary transmission structure includes a primary bearing arranged on the primary exhaust seat, a primary transmission shaft is arranged in the primary bearing, and a primary transmission component is arranged on the primary transmission shaft; the secondary transmission structure includes a secondary bearing arranged on the secondary input end bearing mounting seat, a secondary transmission shaft is arranged in the secondary bearing, and a secondary transmission component is arranged on the secondary transmission shaft; the main shaft transmission component is respectively connected with the primary transmission component and the secondary transmission component.

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