Compressor main body and compressor

Abstract

Embodiments of the present disclosure provide a compressor host and a compressor. The compressor host comprises: a first housing, which is internally provided with a compression chamber and a first bearing chamber, the first bearing chamber having a first opening and being in communication with one end of the compression chamber through the first opening, the first bearing chamber being internally provided with a first bearing, and the first opening being configured to expose at least part of the first bearing to the compression chamber; a first screw and a second screw, which are both disposed in the compression chamber and are in engagement with each other, one end of a first rotating shaft of the first screw extending into the first bearing chamber through the first opening and being supported by the first bearing to rotate; and a first oil supply channel, which is disposed in the first housing, one end of the first oil supply channel being in communication with the first bearing chamber to supply lubricating oil to the first bearing chamber, so that the lubricating oil flows into the compression chamber through at least part of the first bearing exposed to the compression chamber.

Description

Technical Field

[0001] The exemplary embodiments disclosed herein generally relate to the field of compressor technology, and particularly to a compressor host and a compressor. Background Technology

[0002] A twin-screw compressor is a rotary positive displacement compressor that compresses air or other gases by installing two meshing helical rotors or screws (which can be referred to as a male rotor and a female rotor) inside the compression chamber. When the two rotors rotate in opposite directions, gas is drawn into the space between the rotors and the compressor housing (also known as a cavitation chamber) through the inlet. As the cavitation chamber gradually shrinks, the gas is compressed. Finally, the compressed air or gas is discharged through the outlet.

[0003] Twin-screw compressors require lubricating oil during operation. This oil not only lubricates and cools components like the rotors but also seals the gap between the two rotors. However, in traditional twin-screw compressors, the oil injection port in the compression chamber is typically located in the middle of the male and female rotors along the axial direction. The lubricating oil sprayed onto the rotors flows towards the exhaust end as they rotate. This can lead to insufficient lubrication during startup, causing the rotor end near the intake port to overheat, thus affecting the normal operation of the twin-screw compressor.

[0004] This is especially true for twin-screw compressors with a motor-driven female rotor, where the high temperatures at the intake ends of the male and female rotors due to lack of lubrication during startup are even more pronounced. When the motor drives the female rotor, its lower speed results in greater torque and more heat generated by friction. This leads to a faster and higher temperature rise at the intake ends of the male and female rotors, often causing a high-temperature alarm to sound and preventing normal operation of the compressor shortly after startup.

[0005] Furthermore, in existing compressor systems, to ensure the lubrication and cooling of the bearings at both ends of the screw, additional lubrication oil pipes are typically installed on the compressor to provide lubrication to the bearings at both ends of the screw. This lubrication oil circuit results in a complex oil circuit structure for the compressor system and is prone to problems such as lubrication oil leakage due to pipe aging. Utility Model Content

[0006] The purpose of this disclosure is to provide a compressor main unit and a compressor to solve or at least partially solve the aforementioned problems and / or other potential problems existing in conventional compressors (especially compressors with motor-driven female rotor rotation).

[0007] A first aspect of this disclosure provides a compressor main unit. The compressor main unit includes: a first housing having a compression chamber and a first bearing chamber inside, the first bearing chamber having a first opening and communicating with one end of the compression chamber through the first opening, a first bearing being disposed within the first bearing chamber, the first opening being configured to expose at least a portion of the first bearing within the compression chamber; a first screw and a second screw, both disposed within the compression chamber and meshing with each other, one end of a first shaft of the first screw extending into the first bearing chamber through the first opening and supported for rotation by the first bearing; and a first oil supply passage disposed within the first housing, one end of the first oil supply passage communicating with the first bearing chamber to be adapted to supply lubricating oil to the first bearing chamber, such that the lubricating oil flows into the compression chamber through at least a portion of the first bearing exposed within the compression chamber.

[0008] In some embodiments, a flange extending radially inward along a first axis of rotation is provided in the first opening. The flange is located on the side of the first bearing near the compression chamber and supports the first bearing. The flange is configured to define a fluid passage between the compression chamber and the first bearing chamber, so that at least a portion of the first bearing is exposed in the compression chamber.

[0009] In some embodiments, at least a portion of the first bearing is not covered by the axial projection of the flange on the first shaft to form a fluid channel.

[0010] In some embodiments, the flange includes a first portion that extends circumferentially along the first opening and is partially annular.

[0011] In some embodiments, the first portion extends radially inward by a first distance, and the outer periphery of the outer ring of the first bearing and the outer periphery of the inner ring have a second distance in the radial direction, the first distance being greater than or equal to the second distance.

[0012] In some embodiments, a three-dimensional sealing line is provided between the first screw and the second screw, and the projection of the three-dimensional sealing line on the axial direction of the first rotating shaft falls entirely or partially within the first portion.

[0013] In some embodiments, the first housing is further provided with a second bearing chamber that is close to the first bearing chamber and communicates with the compression chamber. The second bearing chamber is provided with a second bearing and a bearing seat. One end of the second shaft of the second screw extends into the second bearing chamber and is supported and rotated by the second bearing. The bearing seat is located on the side of the second bearing that is close to the compression chamber, and the projection of the bearing seat on the axial direction of the second shaft covers the second bearing to limit the second bearing from being exposed in the compression chamber.

[0014] In some embodiments, a three-dimensional sealing line is provided between the first screw and the second screw, and the projection of the three-dimensional sealing line on the axial direction of the first rotating shaft falls entirely into the first part and the bearing seat.

[0015] In some embodiments, the first housing is provided with a radial air inlet communicating with one end of the compression chamber, and the radial air inlet is close to the first bearing chamber.

[0016] In some embodiments, the first screw has a radial air inlet closure line corresponding to the radial air inlet, the radial air inlet closure line including an end point near the first opening, the projection of the end point in the axial direction of the first shaft falling into the first portion.

[0017] In some embodiments, the flange further includes a second portion that extends circumferentially along the first opening and is partially annular.

[0018] In some embodiments, the first portion extends radially inward by a first distance, the outer periphery of the outer ring of the first bearing and the outer periphery of the inner ring have a second distance in the radial direction, the second portion extends radially inward by a third distance, the third distance is less than the first distance, the second distance is less than or equal to the first distance, and the third distance is less than the second distance.

[0019] In some embodiments, the angle at which the first portion extends circumferentially over the first opening falls within the range of 45° to 300°, and / or the sum of the angle at which the first portion extends circumferentially over the first opening and the angle at which the second portion extends circumferentially over the first opening is 360°.

[0020] In some embodiments, the first bearing has a gap extending through both ends of the first bearing so that lubricating oil supplied to the first bearing chamber flows through the gap into the compression chamber.

[0021] In some embodiments, a first oil supply channel is disposed within the first housing along the axial direction of the first rotating shaft, and the other end of the first oil supply channel is located at the axial center of the first housing to facilitate the introduction of lubricating oil from the outside.

[0022] In some embodiments, the first housing is further provided with at least one oil inlet, the at least one oil inlet being close to the middle of the first screw and / or the second screw in the axial direction; and the first housing is further provided with a second oil supply channel, the second oil supply channel being connected to the other end of the first oil supply channel and at least one oil inlet, to be adapted to supply lubricating oil to the first oil supply channel, and to be adapted to supply lubricating oil to the compression chamber via at least one oil inlet.

[0023] In some embodiments, a dynamic seal component sleeved on the first shaft is further disposed in the first bearing chamber, the first bearing is close to the compression chamber, the dynamic seal component is far from the compression chamber, and the first oil supply channel is adapted to deliver lubricating oil between the first bearing and the dynamic seal component.

[0024] In some embodiments, the first housing includes at least a main housing and a first cover. The main housing has a compression chamber and a first opening inside. The first opening extends through to the end face of a first end of the main housing. One end of the first oil supply channel extends through to the end face of the first end. The first cover is connected to the first end to seal the first opening. The end face of the first end and / or the surface of the first cover opposite to the end face is provided with a first groove suitable for communicating the first opening and the first oil supply channel.

[0025] In some embodiments, the size of the first groove is configured such that the flow rate of lubricating oil supplied to the compression chamber through the first oil supply passage accounts for 5%-20% of the total flow rate of lubricating oil supplied to the compression chamber.

[0026] In some embodiments, the first housing is further provided with an exhaust port communicating with the other end of the compression chamber, and the interior of the first housing is further provided with a third bearing chamber near the exhaust port; the third bearing chamber is provided with a third bearing and a fourth bearing, the third bearing being used to support the other end of the first rotating shaft extending into the third bearing chamber, and the fourth bearing being used to support the other end of the second rotating shaft of the second screw extending into the third bearing chamber.

[0027] In some embodiments, the compression chamber is connected to the third bearing chamber via an oil supply channel and an oil return channel, respectively, to be adapted to supply lubricating oil to the third bearing chamber via the oil supply channel and to receive lubricating oil returning from the third bearing chamber via the oil return channel.

[0028] In some embodiments, the compression chamber is connected to the third bearing chamber through a first shaft hole, the other end of the first rotating shaft extends into the third bearing chamber through the first shaft hole, and there is a gap between the first rotating shaft and the first shaft hole to form at least a portion of the oil delivery channel; and / or the compression chamber is connected to the third bearing chamber through a second shaft hole, the other end of the second rotating shaft extends into the third bearing chamber through the second shaft hole, and there is a gap between the second rotating shaft and the second shaft hole to form at least a portion of the oil delivery channel.

[0029] In some embodiments, the first housing is provided with an oil return hole extending through the compression chamber at one end, and the other end of the oil return hole communicating with the third bearing chamber to form at least a partial oil return channel.

[0030] In some embodiments, the first housing includes a main housing having a compression chamber inside and a second cover connected to a second end of the main housing; the second end has a second opening suitable for accommodating a third bearing and / or a third opening suitable for accommodating a fourth bearing, the second opening and / or the third opening forming at least a portion of the third bearing chamber; and the other end of the oil return hole extends through to the end face of the second end; the oil return channel also includes a second groove formed on the end face of the second end, the second groove communicating with the second opening and / or the third opening, and the oil return hole communicating with the second groove.

[0031] A second aspect of this disclosure provides a compressor. The compressor includes a motor and a compressor main unit as described in the first aspect, wherein a first screw of the compressor main unit is a female screw, a second screw of the compressor main unit is a male screw, and the motor is drively connected to the female screw.

[0032] In some embodiments, the motor includes a second housing, a stator, and a rotor. The stator is fixed inside the second housing, and the rotor is housed in the hollow cavity of the stator. One end of the first shaft of the first screw extends into the second housing, and the rotor is deployed on the first shaft of the first screw. The second housing is directly connected to the first housing.

[0033] It should be understood that the content described in this content section is not intended to limit the key or essential features of the embodiments of this disclosure, nor is it intended to restrict the scope of this disclosure. Other features of this disclosure will become readily apparent from the following description. Attached Figure Description

[0034] The above and other features, advantages, and aspects of the embodiments of this disclosure will become more apparent from the accompanying drawings and the following detailed description. In the drawings, the same or similar reference numerals denote the same or similar elements, wherein: Figure 1 A first cross-sectional view of a compressor main unit according to some embodiments of the present disclosure is shown; Figure 2 A perspective sectional view of a compressor main unit according to some embodiments of the present disclosure is shown; Figure 3 A second cross-sectional view of a compressor main unit according to some embodiments of the present disclosure is shown; Figure 4 A third cross-sectional view of a compressor main unit according to some embodiments of the present disclosure is shown; Figure 5 A fourth cross-sectional view of a compressor main unit according to some embodiments of the present disclosure is shown; Figure 6 A simplified structural diagram of a flange according to some embodiments of the present disclosure is shown; Figure 7 A perspective view of a portion of the structure of the main housing according to some embodiments of the present disclosure is shown; Figures 8 to 10 Simplified structural diagrams of flanges according to other embodiments of the present disclosure are shown respectively; Figure 11 A side view of the main housing according to some embodiments of the present disclosure is shown; Figure 12 and Figure 13 Simplified structural diagrams of flanges according to further embodiments of the present disclosure are shown respectively; Figure 14A partial cross-sectional view of a compressor main unit according to some embodiments of the present disclosure is shown; Figure 15 A side view of a first cover according to some embodiments of the present disclosure is shown; Figure 16 A partial cross-sectional view of a compressor main unit according to some embodiments of the present disclosure is shown; and Figure 17 A cross-sectional view of a compressor according to some embodiments of the present disclosure is shown.

[0035] Explanation of reference numerals in the attached figures: 100 - Compressor main unit; 110 - First shell; 111 - Main shell; 112 - First cover; 113 - Second cover; 114 - First end; 115 - Second end; 121 - Compression chamber; 122 - Radial air inlet; 123 - Exhaust port; 124 - Oil inlet; 125 - Projection; 126 - Radial air inlet closing line; 127 - End point; 128 - First space; 129 - Second space; 130 - First bearing chamber; 131 - First opening; 132 - Inner circumferential surface; 133 - Flange; 134 - First part; 135 - Second part; 136 - First groove; 137 - Recess; 138 - Through hole; 140 - Second bearing housing; 141 - Bearing housing; 150 - Third bearing chamber; 151 - First shaft hole; 152 - Second shaft hole; 153 - Oil return hole; 154 - Second opening; 155 - Third opening; 156 - Second groove; 160 - First screw; 161 - First shaft; 162 - First bearing; 163 - Outer ring; 164 - Inner ring; 165 - Rolling element; 166 - Clearance; 167 - Dynamic seal; 168 - Third bearing; 170 - Second screw; 171 - Second shaft; 172 - Second bearing; 173 - Fourth bearing; 181 - First fuel supply channel; 182 - Second fuel supply channel; and 200 - Motor; 210 - Second housing; 220 - Stator; 221 - Hollow inner cavity; 230 - Rotor. Detailed Implementation

[0036] Preferred embodiments of the present disclosure will now be described in more detail with reference to the accompanying drawings. While preferred embodiments of the present disclosure are shown in the drawings, it should be understood that the present disclosure may be implemented in various forms and should not be limited to the embodiments set forth herein. Rather, these embodiments are provided so that the present disclosure will be thorough and complete, and will fully convey the scope of the present disclosure to those skilled in the art.

[0037] The term "comprising" and its variations as used herein signify open inclusion, i.e., "including but not limited to". Unless otherwise stated, the term "or" means "and / or". The term "based on" means "at least partially based on". The terms "one example embodiment" and "one embodiment" mean "at least one example embodiment". The term "another embodiment" means "at least one additional embodiment". The terms "first", "second", etc., may refer to different or the same objects.

[0038] As mentioned earlier, a twin-screw compressor is a rotary positive displacement compressor that compresses air or other gases by installing two meshing helical rotors or screws (which can be referred to as a male rotor and a female rotor) within a compression chamber. When the two rotors disengage, the volume of the cavitation cavity between the two rotors in the compression chamber continuously expands, and air or gas enters the cavitation cavity through the inlet (inlet step). As the rotors continue to rotate, the volume of the cavitation cavity continues to expand until it reaches its maximum volume, and then the volume of the cavitation cavity shrinks again. Near this maximum volume point, when the trailing edge of a tooth on the rotor crosses the edge of the inlet, the cavitation cavity defined by the tooth is separated from the inlet (closing step). As the rotors continue to rotate, the cavitation cavity containing the trapped air or gas moves axially along the screw. During this process, the volume of the cavitation cavity continuously shrinks, causing the internal pressure to continuously increase. This is a continuous positive displacement process (compression step). As the rotors continue to rotate, the cavitation cavity containing the trapped air or gas forms fluid communication with the exhaust port, and the compressed air or gas is forced to be discharged outside the compression chamber (discharge step). The advantage of screw compressors is that they can generate a continuous and relatively pulse-free compressed airflow.

[0039] Twin-screw compressors require lubricating oil during operation. This oil not only lubricates and cools components like the rotors but also seals the gap between the two rotors. In practical applications, the compressor is typically connected to an oil-gas separator. The oil-gas separator supplies lubricating oil to the compressor, and the oil in the compressor is discharged into the oil-gas separator along with the compressed air or gas. The oil-gas separator separates the lubricating oil from the compressed air or gas and uses air pressure to return it to the compressor, forming a lubricating oil circulation loop.

[0040] Traditional twin-screw compressors typically have multiple oil injection holes in the axial center of the casing. These holes are positioned opposite the male and female rotors, respectively, and lubricating oil supplied by the oil-gas separator is injected into the compression chamber through these holes. However, during the initial startup phase (also known as the "initial stage"), the pressure in the oil-gas separator is insufficient, resulting in a limited supply of lubricating oil. Furthermore, a small amount of lubricating oil flows with the airflow towards the outlet end of the compression chamber, leaving the inlet end lacking lubricating oil. This lack of lubricating oil can easily lead to high temperatures at the inlet end of the rotor. This is especially true for female-rotor driven twin-screw compressors, which generate more heat than male-rotor driven compressors due to their lower rotor speed and higher torque, making them more prone to overheating and potentially causing the compressor to malfunction.

[0041] To address, or at least partially address, the aforementioned problems or other potential problems existing in conventional compressor technology, particularly female rotor-driven compressors, embodiments of this disclosure provide a compressor main unit. In this improved solution, the compressor main unit includes a first housing, a first screw, a second screw, and a first oil supply passage. The first housing contains a compression chamber and a first bearing chamber. The first bearing chamber has a first opening and communicates with one end of the compression chamber through the first opening. A first bearing is disposed within the first bearing chamber, and the first opening is configured to expose at least a portion of the first bearing within the compression chamber. Both the first screw and the second screw are disposed within the compression chamber and mesh with each other. One end of the first shaft of the first screw extends into the first bearing chamber through the first opening and is supported for rotation by the first bearing. The first oil supply passage is disposed within the first housing, and one end of the first oil supply passage communicates with the first bearing chamber to provide lubricating oil to the first bearing chamber, allowing the lubricating oil to flow into the compression chamber through at least a portion of the first bearing exposed within the compression chamber.

[0042] In embodiments of this disclosure, the first bearing chamber communicates with the compression chamber via a first opening, and at least a portion of the first bearing is exposed in the compression chamber via the first opening. A fluid channel passing through the first bearing chamber can be formed between the first bearing chamber and the compression chamber. Lubricating oil can be supplied to the first bearing chamber through the first oil supply channel, which not only lubricates and cools components such as the first bearing in the first bearing chamber, but also allows the lubricating oil to flow into the compression chamber through the fluid channel to lubricate and cool the first and second screws. This helps to reduce the temperature of the ends of the first and second screws near the first bearing chamber (e.g., the ends near the radial air inlet). Especially in the initial stage after the compressor starts up, it can prevent the ends of the first and second screws near the first bearing chamber from becoming too hot. Moreover, this design eliminates the need for separate pipelines to supply lubricating oil to the compression chamber and bearing chamber, simplifying the compressor's piping structure.

[0043] Figure 1A first cross-sectional view of a compressor main unit according to some embodiments of the present disclosure is shown. Figure 2 A perspective sectional view of a compressor main unit according to some embodiments of the present disclosure is shown. Figure 2 A portion of the first casing is cut away to reveal its internal structure. It should be noted that this first sectional view, as well as the second, third, and so on, are merely used to distinguish different sections of the compressor main unit and do not constitute any limitation on the structure of the compressor main unit.

[0044] See Figure 1 and Figure 2 As shown, the compressor main unit 100 of the embodiments of this disclosure includes a first housing 110, a first screw 160, a second screw 170, and a first oil supply passage 181. Each of these components will be described in detail below.

[0045] The first housing 110 has a compression chamber 121 and a first bearing chamber 130 inside. The first bearing chamber 130 has a first opening 131 and communicates with the compression chamber 121 through the first opening 131. A first bearing 162 is disposed inside the first bearing chamber 130. See also, as an example. Figure 2 As shown, the first opening 131 can be a cylindrical hole, that is, the cross-section of the first opening 131 can be circular. The first bearing 162 can be disposed within the first opening 131. Of course, the first opening 131 can also be of other shapes, and the first bearing 162 can also be disposed in other positions of the first bearing chamber 130. The embodiments of this disclosure are not limited in this respect.

[0046] In some embodiments, see Figure 1 and Figure 2 As shown, the first housing 110 may include a main housing 111 and a first cover 112. The main housing 111 has a compression chamber 121 and a first opening 131 inside. The main housing 111 has a first end 114 and a second end 115 opposite to each other. The first opening 131 extends to the end face of the first end 114 of the main housing 111. The first cover 112 is connected to the first end 114 and covers the first opening 131, so as to define the first bearing chamber 130 together with the main housing 111.

[0047] In some embodiments, the first housing 110 may further be provided with a radial air inlet 122 and an exhaust outlet 123 communicating with the compression chamber 121. The radial air inlet 122 may be close to the first bearing chamber 130, and the radial air inlet 122 may be communicated with the end of the compression chamber 121 near the first bearing chamber 130 (which may also be referred to as the air inlet end in some cases). The exhaust outlet 123 may be communicated with the end of the compression chamber 121 away from the first bearing chamber 130 (which may also be referred to as the exhaust end in some cases).

[0048] The first screw 160 and the second screw 170 are both disposed within the compression chamber 121 and mesh with each other. One end of the first shaft 161 of the first screw 160 extends into the first bearing chamber 130 via the first opening 131 and is supported for rotation by the first bearing 162. In some examples, combined Figure 1 As shown, the first screw 160 can be a female screw, which can be mounted on the first rotating shaft 161. The second screw 170 can be a male screw, which can be mounted on the second rotating shaft 171 parallel to the first rotating shaft 161. The interaction between the male and female screws achieves the purpose of compressing air or gas. Alternatively, the first screw 160 can be a male screw, and the second screw 170 can be a female screw.

[0049] Figure 3 A second cross-sectional view of a compressor main unit 100 according to some embodiments of the present disclosure is shown. See also Figure 3 As shown, in some embodiments, a second bearing chamber 140 may be provided inside the first housing 110, close to the first bearing chamber 130 and communicating with the compression chamber 121. A second bearing 172 is provided inside the second bearing chamber 140. One end of the second shaft 171 of the second screw 170 extends into the second bearing chamber 140 and is supported for rotation by the second bearing 172.

[0050] Figure 4 A third cross-sectional view of a compressor main unit 100 according to some embodiments of the present disclosure is shown. See also Figure 4 In some embodiments, the first housing 110 may further include a third bearing chamber 150 communicating with the other end of the compression chamber 121. The third bearing chamber 150 may contain a third bearing 168 and a fourth bearing 173. The other end of the first rotating shaft 161 may extend into the third bearing chamber 150 and be supported by the third bearing 168, and the other end of the second rotating shaft 171 may extend into the third bearing chamber 150 and be supported by the fourth bearing 173. Thus, the first screw 160 and the second screw 170 can be stably installed within the first housing 110.

[0051] In some embodiments, the first opening 131 may be configured to expose at least a portion of the first bearing 162 to the compression chamber 121, forming a fluid passage through the first bearing 162 between the first bearing chamber 130 and the compression chamber 121. A first oil supply passage 181 is disposed within the first housing 110. One end of the first oil supply passage 181 communicates with the first bearing chamber 130 to provide lubricating oil to the first bearing chamber 130, allowing the lubricating oil to flow into the compression chamber 121 via at least a portion of the first bearing 162 exposed in the compression chamber 121. In this way, the lubricating oil provided by the first oil supply passage 181 can lubricate and cool not only the first bearing 162, but also the first screw 160 and the second screw 170. Especially in the initial stage after the compressor main unit 100 is started, it is possible to prevent the ends of the first screw 160 and the second screw 170 near the air inlet from becoming too hot.

[0052] In some examples, the first bearing 162 may have a gap 166 extending through both ends of the first bearing 162. For example, in combination Figure 3 As shown, the first bearing 162 may include an outer ring 163, an inner ring 164 disposed inside the outer ring 163, and a plurality of rolling elements 165 (e.g., spherical rollers, cylindrical rollers, tapered rollers, etc.) disposed between the outer ring 163 and the inner ring 164. There may be gaps 166 between adjacent rolling elements 165, and these gaps 166 may extend through both ends of the first bearing 162. In some cases, this type of bearing may also be referred to as an "open bearing".

[0053] In some embodiments, combined with Figures 1 to 3 As shown, a flange 133 extending radially inward along the first shaft 161 may be provided within the first opening 131. The flange 133 is located on the side of the first bearing 162 near the compression chamber 121. At least a portion of the first bearing 162 is not covered by the axial projection of the flange 133 onto the first shaft 161, thus exposing it to the compression chamber 121. In other words, the flange 133 may be configured to define a fluid passage between the compression chamber 121 and the first bearing chamber 130, so that at least a portion of the first bearing 162 is exposed to the compression chamber 121. Thus, not only can lubricating oil in the first bearing chamber 130 enter the compression chamber 121 via the fluid passage to lubricate and cool the first screw 160, but during the rotation of the first screw 160, lubricating oil can also be splashed from the compression chamber 121 onto the first bearing chamber 130 to lubricate and cool the first bearing 162.

[0054] In some embodiments, flange 133 axially supports first bearing 162. Flange 133 may contact first bearing 162, for example, flange 133 may serve as a stop structure for mounting first bearing 162 in first opening 131. Flange 133 may also be close to first bearing 162 but not in contact with it; for example, the distance between flange 133 and first bearing 162 may fall within the range of 0 to 1 cm, or within the range of 1 micrometer to 1 cm. Preferably, the distance between flange 133 and first bearing 162 is less than or equal to 50% of the diameter of first shaft 161.

[0055] Figure 5 A fourth cross-sectional view of a compressor main unit 100 according to some embodiments of the present disclosure is shown. Figure 6 A simplified structural diagram of the flange 133 according to some embodiments of the present disclosure is shown. See also Figure 5 and Figure 6 As shown, in some embodiments, the flange 133 may be present within a limited angular range (e.g., within angular range α) surrounding the first pivot 161, and absent outside this angular range (e.g., within angular range β). In this case, a fluid passage is defined between the inner circumferential surface 132 of the first opening 131 not covered by the flange 133 and the corresponding outer circumferential surface of the first pivot 161.

[0056] Alternatively, the flange 133 may exist across the entire angular range (i.e., 360°) around the first pivot 161. For example, the flange 133 may extend circumferentially on the inner circumferential surface 132 of the first opening 131, forming a closed annular flange 133. In this case, at least a portion of the inner circumference of the flange 133 defines a fluid passage between at least a portion of the outer circumferential surface of the first pivot 161. In some examples, the flange 133 may have a non-constant radially inward extension distance when viewed from the entire circumference of the inner surface of the first opening 131. That is, the radially inward extension distance of different portions of the flange 133 in the circumferential direction of the first opening 131 may be different. As an example, the flange 133 may include at least two portions sequentially connected along the circumference of the first opening 131. Each of these at least two portions may have a constant radially inward extension distance, and the radially inward extension distances of different portions may be different.

[0057] In some embodiments, combined with Figure 5 and Figure 6As shown, flange 133 includes a first portion 134 extending circumferentially along the first opening 131 and forming a partial annular (or C-shape). The first portion 134 may include an inner edge, two side edges, and an outer edge. The outer edge of the first portion 134 may connect to the inner peripheral surface 132 of the first opening 131, and the two ends of the inner edge of the first portion 134 may connect to the two side edges. The two side edges of the first portion 134 may extend radially or substantially radially toward the inner peripheral surface 132 of the first opening 131. If flange 133 includes only the first portion 134, both side edges of the first portion 134 are in contact with the inner peripheral surface 132 of the first opening 131.

[0058] In some embodiments, combined with Figure 6 As shown, the first portion 134 extends radially inward by a first distance (e.g., R1). The outer peripheral surface of the outer ring 163 of the first bearing 162 is in contact with the inner peripheral surface 132 of the first opening 131. A second radial distance (e.g., R2) exists between the outer peripheral portion of the outer ring 163 and the outer peripheral portion of the inner ring 164. The first distance R1 is greater than or equal to the second distance R2. In some examples, the first portion 134 may extend radially inward to near the outer peripheral surface of the first shaft 161, and a gap exists between the inner edge of the first portion 134 and the outer peripheral surface of the first shaft 161. For example, the radial dimension of this gap may fall within the range of 1 micrometer to 1 millimeter, and the radial dimension of this gap may be constant. That is, the radial width of this gap may remain unchanged.

[0059] In some embodiments, continue to combine Figure 6 As shown, the angle at which the first portion 134 extends circumferentially from the first opening 131 can fall within the range of 45° to 300° (e.g., 120°). In some examples, the first portion 134 may be entirely located in the lower half of the first opening 131, or primarily located in the lower half of the first opening 131. Alternatively, the first portion 134 may be entirely located in the upper half of the first opening 131, or primarily located in the upper half of the first opening 131.

[0060] In some embodiments, flange 133 may completely or almost completely (e.g., greater than 98%, or greater than 99%) cover a specific angular range of the first bearing 162. In some embodiments, combined with Figure 5As shown, a three-dimensional (3D) sealing line exists between the first screw 160 and the second screw 170. This specific angular range can include an angular range capable of covering the 3D sealing line. That is, the two-dimensional (2D) projection 125 of the 3D sealing line in the axial direction of the first rotating shaft 161 can fall wholly or partially within the range of the flange 133, for example, within the first portion 134. It should be noted that, for a specific model of twin-screw compressor, the 2D projection of the 3D sealing line in the axial direction is generally fixed. At some angles, the 3D sealing line is a fixed curve. During the rotation of the two screws, the 3D sealing line moves axially at a specific speed and tilt angle, thereby ensuring that the 2D projection of the 3D sealing line of a specific model of twin-screw compressor is generally fixed. In this way, it is possible to prevent the escape of compressed gas or air from the cavitation defined by the two screws.

[0061] Alternate or additional land, in combination Figure 3 and Figure 5 As shown, a bearing housing 141 may also be provided inside the second bearing chamber 140. The bearing housing 141 is located on the side of the second bearing 172 near the compression chamber 121, and the axial projection of the bearing housing 141 covers the second bearing 172, thereby limiting the exposure of the second bearing 172 in the compression chamber 121. The axial projection of the 3D sealing line can fall entirely into the first part 134 and the bearing housing 141 to prevent the escape of compressed gas or air.

[0062] Figure 7 A perspective view of a portion of the structure of the main housing 111 according to some embodiments of the present disclosure is shown. Figure 7As shown, in some embodiments, the first screw 160 has a radial air inlet closing line 126 corresponding to the radial air inlet 122, the radial air inlet closing line including an end point 127 near the first opening 131. The axial projection of the end point 127 corresponds to a specific angle of the first bearing 162. The second screw 170 also has a radial air inlet closing line corresponding to the radial air inlet 122, the axial projection of the end point of the radial air inlet closing line of the second screw 170 corresponding to a specific angle of the second bearing 172. In some cases, the radial air inlet closing line 126 of the first screw 160 and the radial air inlet closing line of the second screw 170 may correspond to each other. When the first screw 160 and the second screw 170 rotate synchronously to their respective corresponding specific angles, the gas or air in the cavitation is completely sealed, and the gas or air in the radial air inlet 122 can no longer flow into the cavitation. The specific angle range mentioned above may also include the specific angle that covers the first bearing 162 corresponding to the end point 127. That is, the projection of this endpoint in the axial direction of the first rotating shaft 161 can fall within the range of the flange 133 (e.g., within the first portion 134), or be close to the flange 133 (e.g., less than 1 cm or less than 1 mm). In this way, it is possible to prevent gas or air from escaping from the cavitation. It is understood that in practical applications, this specific angular range can be an angular range that covers the axial projection of the 3D sealing line and the axial projection of the endpoint of the radial air inlet 122 sealing line.

[0063] It should be noted that the above-mentioned section 134 is merely an example. The following will combine... Figures 8 to 10 Some other alternative embodiments of flange 133 are illustrated by way of example. Figure 8 The illustrated embodiments and Figure 6 The illustrated embodiment is similar, and is a version with its axial rotation. Figure 8 In the illustrated embodiment, a large portion (e.g., more than 95%) of the first portion 134 is located in the upper half of the first opening 131.

[0064] Figure 9 The illustrated embodiments and Figure 6 The illustrated embodiments are similar in that the flanges 133 all include a first portion 134, but... Figure 9 The angle range corresponding to the first part 134 in the middle is greater than Figure 6 The first part, 134, corresponds to the angle range. For example, in... Figure 9 In one embodiment, the angle range corresponding to the first portion 134 may be 260°, and most of the first portion 134 (e.g., more than 60%) is located in the lower half of the first opening 131.

[0065] Figure 10 The illustrated embodiments and Figure 8The illustrated embodiments are similar, but in Figure 10 In the illustrated embodiment, the first portion 134 is provided with one or more through-holes 138 extending through the first portion 134 along an axial direction parallel to the first opening 131. In this manner, the one or more through-holes 138 can form at least a partial fluid passage, allowing lubricating oil in the first bearing chamber 130 to flow into the compression chamber 121 via the one or more through-holes 138. In some examples, the one or more through-holes 138 may be located outside a specific angular range of the first rotating shaft 161 to prevent compressed gas or air in the compression chamber 121 from escaping via the one or more through-holes 138.

[0066] Figure 11 A side view of the main housing 111 according to some embodiments of the present disclosure is shown. Specifically, Figure 11 A side view is shown from the first end 114 of the main housing 111. Figure 12 A simplified structural diagram of the flange 133 according to further embodiments of the present disclosure is shown. See also Figure 11 and Figure 12 As shown, in some embodiments, the flange 133 further includes a second portion 135 extending circumferentially along the first opening 131 and forming a partial annular shape. The second portion 135 may include an outer edge that contacts the inner circumferential surface 132 of the first opening 131 and an inner edge opposite to the outer edge. The outer edge and inner edge of the second portion 135 may have a constant radially inward extending distance, which may be referred to as a third distance R3. The third distance R3 may be smaller than the first distance R1, and the third distance R3 is also smaller than the second distance R2 between the outer circumferential surface of the outer ring 163 and the outer circumferential surface of the inner ring 164 of the first bearing 162. In this way, two discrete constant radially inward extending distances, namely the first distance R1 and the third distance R3, can be formed on the inner circumferential surface 132 of the first opening 131. In this case, at least the inner edge of the second portion 135 can define a fluid passage between it and the outer circumferential surface of the first shaft 161.

[0067] In some embodiments, the sum of the angle at which the first portion 134 extends circumferentially from the first opening 131 and the angle at which the second portion 135 extends circumferentially from the first opening 131 is 360°. In this case, the two ends of the second portion 135 are respectively connected to the two ends of the first portion 134, and the two ends of the inner edge of the second portion 135 are respectively connected to the two side edges of the first portion 134. Thus, the first portion 134 and the second portion 135 can support the first bearing 162 in the entire circumferential direction (i.e., within a 360° angle range), which facilitates the installation of the first bearing 162 and helps to improve the stability of the first bearing 162.

[0068] As an example, combined Figure 12As shown, the first part 134 can exist within an angular range α (e.g., 120°) around the first axis of rotation 161, and the second part 135 can exist within an angular range β (e.g., 240°) around the second axis of rotation 171. The sum of the angular range α and the angular range β is 360°. The angular range α and the angular range β can also be referred to as conjugate angles.

[0069] As another example, combining Figure 13 As shown, Figure 13 The illustrated embodiments and Figure 12 The difference in the illustrated embodiment lies in the angle range corresponding to the first part 134 and the second part 135, respectively. Figure 13 The angle range corresponding to the first part 134 in the middle is greater than Figure 12 The first part 134 corresponds to the angle range, for example in Figure 13 The angle range corresponding to the first part 134 in the figure can be 260° (and) Figure 9 The illustrated embodiments are similar. Figure 13 The second part, 135, corresponds to an angle range smaller than... Figure 12 The second part, 135, corresponds to the angle range, for example, in Figure 13 The angle range corresponding to the second part 135 can be 100°.

[0070] It should be understood that the structure of the second part 135 described above is merely exemplary. Alternatively, the inner edge of the second part 135 does not necessarily have to be arc-shaped; other shapes can be used, such as the inner periphery of the second part 135, which can adopt any suitable shape capable of effectively supporting the first bearing 162. Alternatively, one end of the second part 135 is connected to one end of the first part 134, and the other end of the second part 135 is separate from the other end of the first part 134. Alternatively, the second part 135 and the first part 134 can also be independent of each other. That is, neither end of the second part 135 is connected to either end of the first part 134. The embodiments of this disclosure are not limited in this respect.

[0071] In some embodiments, the inner circumferential surface 132 of the first opening 131 may have an annular region corresponding to and extending circumferentially from the first portion 134. This annular region can be understood as the area where the plane defined by the inner circumferential surface 132 of the first opening 131 intersects with that defined by the first portion 134. This annular region may include a first region containing the first portion 134 and a second region outside the first portion 134. One or more support structures extending radially inward may be provided in the second region. These one or more support structures may serve as alternative structures to the second portion 135 mentioned above. For example, these one or more support structures may include one or more (e.g., regularly distributed) protrusions to support the first bearing 162 and / or act as stops for the first bearing 162 during installation.

[0072] In some embodiments, combined with Figure 1 As shown, the first oil supply channel 181 can be arranged axially within the first housing 110 along the first rotating shaft 161, and the other end of the first oil supply channel 181 is located at the axial center of the first housing 110 to facilitate the introduction of lubricating oil from the outside. As an example, the other end of the first oil supply channel 181 can be connected to an external oil supply device (e.g., an oil-gas separator) to introduce lubricating oil from the outside.

[0073] In some embodiments, combined with Figure 1 As shown, the first housing 110 also has at least one oil inlet 124, which is located near the axial center of the first screw 160 and / or the second screw 170. The first housing 110 also has a second oil supply channel 182, which is connected to the other end of the first oil supply channel 181 and the at least one oil inlet 124, to provide lubricating oil to the first oil supply channel 181 and to provide lubricating oil to the compression chamber 121 via the at least one oil inlet 124. As an example, the second oil supply channel 182 may extend in a direction perpendicular to the first oil supply channel 181, one end of which may be used to connect to an oil supply device such as an oil-gas separator, and the other end of which may communicate with the other end of the first oil supply channel 181. The at least one oil inlet 124 can be arranged sequentially at intervals along the extension direction of the second oil supply channel 182. For example, it can include an oil inlet 124 opposite to the first screw 160 and an oil inlet 124 opposite to the second screw 170. One end of each oil inlet 124 extends into the second oil supply channel 182 to receive lubricating oil from the second oil supply channel 182. The other end of each oil inlet 124 extends into the compression chamber 121 to spray lubricating oil into the compression chamber 121. Thus, oil is supplied not only from the intake end to the compression chamber 121, but also from the middle of the compression chamber 121, ensuring that different parts of the two screws are in full contact with the lubricating oil to guarantee cooling, lubrication, and sealing effects.

[0074] Figure 14 A partially enlarged view of a compressor main unit 100 according to some embodiments of the present disclosure is shown. (In conjunction with...) Figure 14 As shown, in some embodiments, a dynamic seal 167 is also disposed within the first bearing chamber 130, and the dynamic seal 167 is fitted onto the first rotating shaft 161. The first bearing 162 is close to the compression chamber 121, and the dynamic seal 167 is away from the compression chamber 121. The first oil supply passage 181 can be configured to deliver lubricating oil between the first bearing 162 and the dynamic seal 167. In other words, the first bearing 162 can be disposed between the flange 133 and the dynamic seal 167, and the first oil supply passage 181 can deliver lubricating oil between the first bearing 162 and the dynamic seal 167. In this way, lubricating oil can be prevented to some extent from overflowing from the first rotating shaft 161 to the outside of the first bearing chamber 130. The dynamic seal 167 can be any suitable component capable of achieving a seal during the rotation of the first rotating shaft 161, such as a lip seal.

[0075] Figure 15 A side view of a first cover 112 according to some embodiments of the present disclosure is shown. (In conjunction with...) Figure 15 As shown, in some embodiments, the first bearing chamber 130 may include a first opening 131 and a recess 137 (also referred to as a cavity or secondary hole) disposed in the first cover 112. When the first cover 112 is connected to the first end 114 of the main housing 111, the recess 137 may be opposite to and communicate with the first opening 131. The recess 137 may accommodate the dynamic sealing component 167. Preferably, the recess 137 may be annular. As an example, the middle of the first cover 112 may be provided with a hole for the first rotating shaft 161 to pass through, the recess 137 may surround the hole, and the recess 137 may communicate with the hole. In this way, the assembly and maintenance of the first bearing 162 and the dynamic sealing component 167 can be facilitated.

[0076] In some examples, a bushing structure (e.g., an annular structure) may also be provided between the main housing 111 and the first cover 112 to simplify the assembly process and improve compressor performance. To ensure proper installation of the dynamic seal 167, when the first cover 112 needs to be installed, the first shaft 161 can be installed from the side where the compression chamber 121 is located, and the dynamic seal 167 can be installed into the recess 137 of the first cover 112 from the other side. The bushing structure can also be installed on the first cover 112 on the other side. This bushing structure employs a hardened structure to prevent or reduce brittle wear. In this case, it is not necessary to perform overall hardening treatment on the entire first screw 160 or the first shaft 161. Alternatively, the first bearing chamber 130 may also include one or more secondary holes coinciding with the axis of the first opening 131, the diameter of which may be larger or smaller than the diameter of the first opening 131. Other components, such as the dynamic seal 167, can be accommodated using these one or more secondary holes.

[0077] Combination Figure 11 and Figure 14 As shown, in some embodiments, one end of the first oil supply channel 181 can extend to the end face of the first end 114 of the main housing 111. The end face of the first end 114 can have a first groove 136, which communicates with the first opening 131 and the first oil supply channel 181 respectively. Thus, the first oil supply channel 181 delivers lubricating oil to the first end 114 of the main housing 111, and delivers the lubricating oil to the first opening 131 via the first groove 136. As an example, combined with... Figure 11 As shown, the first groove 136 can extend radially along the first opening 131.

[0078] Alternate or additional land, in combination Figure 15 As shown, the first groove 136 can also be deployed on the surface of the first cover 112 opposite to the end face of the first end 114. For example, the first groove 136 can extend radially along the first cover 112, one end of the first groove 136 can communicate with the recess 137, and the other end of the first groove 136 extends to a position opposite to one end of the first oil supply channel 181. When the first cover 112 is connected to the first end 114, the other end of the first groove 136 communicates with one end of the first oil supply channel 181. Of course, in some cases, two first grooves 136 can be provided on the end face of the first end 114 and the first cover 112 respectively, and the two first grooves 136 can be arranged opposite to each other.

[0079] In some embodiments, the dimensions of the first groove 136 can be configured such that the flow rate of lubricating oil supplied to the compression chamber 121 through the first oil supply channel 181 accounts for 5%-20% of the total flow rate of lubricating oil supplied to the compression chamber 121. For example, the cross-sectional area of ​​the first groove 136 and the cross-sectional area of ​​the second oil supply channel 182 can have a specific proportional relationship, such that 5% to 20% (e.g., 10%) of the total flow rate of the second oil supply channel 182 flows into the first opening 131 via the first groove 136. In this way, the oil passage structure of the compressor host 100 can be simplified.

[0080] Figure 16 A partial cross-sectional view of a compressor main unit 100 according to some embodiments of the present disclosure is shown. In some embodiments, in conjunction with Figure 4 and Figure 16 As shown, the compression chamber 121 is connected to the third bearing chamber 150 via an oil supply channel and an oil return channel. The oil supply channel can be configured to deliver lubricating oil from the compression chamber 121 to the third bearing chamber 150 by means of the pressure difference between the compression chamber 121 and the third bearing chamber 150, to lubricate the third bearing 168 and / or the fourth bearing 173 in the third bearing chamber 150. The oil return channel can also be configured to return lubricating oil from the third bearing chamber 150 to the compression chamber 121 by means of the pressure difference between the third bearing chamber 150 and the compression chamber 121. In this way, it is no longer necessary to deploy a separate oil supply line for the third bearing chamber 150, which helps to simplify the oil circuit structure of the compressor main unit 100.

[0081] In some examples, combined Figure 16As shown, the compression chamber 121 may include a first space 128 and a second space 129. The first space 128 may be jointly defined by the first screw 160 and the second screw 170 and the side wall of the compression chamber 121 near the radial inlet 122, and the second space may be jointly defined by the first screw 160 and the second screw 170 and the side wall of the compression chamber near the exhaust port 123. Referring to the plane jointly defined by the first screw 160 and the second screw 170, the first space 128 is located on the side of this plane near the radial inlet 122, and the second space 129 is located on the side of this plane near the exhaust port 123. During the operation of the compressor main unit 100, the first screw 160 and the second screw 170 rotate in opposite directions, and the cavitation moves axially and gradually approaches the exhaust port 123. Finally, the cavitation communicates with the exhaust port 123 via the second space 129 and discharges compressed gas. As compressed gas is discharged, the gas pressure in the tooth grooves of the first screw 160 and the second screw 170 gradually decreases, and then rotates to the side opposite to the exhaust port 123. This operation results in the pressure in the second space 129 near the exhaust port 123 being higher than the pressure in the first space 128 away from the exhaust port 123. In this case, the oil delivery channel can be configured to communicate with or be close to the second space 129, and the oil return channel can be configured to communicate with or be close to the first space 128. In this way, the pressure in the second space 129 is higher than the pressure in the third bearing chamber 150, and the pressure in the first space 128 is lower than the pressure in the third bearing chamber 150, which is beneficial to promote the flow of lubricating oil and improve lubrication and cooling effects. This lubrication method does not require additional lubricating oil pipelines outside the compressor, simplifying the compressor's oil circuit system, saving costs, and avoiding problems such as oil circuit aging and lubricating oil leakage that occur with additional lubricating oil pipelines in the prior art.

[0082] In some embodiments, combined with Figure 1 As shown, the compression chamber 121 can communicate with the third bearing chamber 150 through the first shaft hole 151. The other end of the first rotating shaft 161 extends into the third bearing chamber 150 through the first shaft hole 151, and there is a gap between the first rotating shaft 161 and the first shaft hole 151 to form at least a partial oil delivery channel. Under the pressure difference between the second space 129 and the third bearing chamber 150, the lubricating oil in the compression chamber 121 can flow into the third bearing chamber 150 through the gap between the first rotating shaft 161 and the first shaft hole 151. In this way, there is no need to separately provide a hole for forming an oil delivery channel, which helps to simplify the structure of the compressor main unit 100.

[0083] As an example, combined Figure 4 and Figure 16As shown, the first housing 110 may further include a second cover 113. A second opening 154 may be formed at the second end 115 of the main housing 111. One end of the second opening 154 extends through to the end face of the second end 115, and the other end of the second opening 154 communicates with the compression chamber 121 through the first shaft hole 151. The second cover 113 is connected to the second end 115 and at least seals the second opening 154 to form a third bearing chamber 150. A third bearing 168 may be disposed within the second opening 154. The other end of the first rotating shaft 161 may extend into the second opening 154 through the first shaft hole 151 and be supported by the third bearing 168 within the second opening 154. Lubricating oil in the compression chamber 121 may flow into the second opening 154 through the gap between the first rotating shaft 161 and the first shaft hole 151, directly lubricating the third bearing 168.

[0084] Alternate or additional land, in combination Figure 16 As shown, the compression chamber 121 can also communicate with the third bearing chamber 150 through the second shaft hole 152. The other end of the second rotating shaft 171 extends into the third bearing chamber 150 through the second shaft hole 152. There is a gap between the second rotating shaft 171 and the second shaft hole 152 to form at least a partial oil supply channel. In this way, the lubricating oil flowing in through the gap between the first rotating shaft 161 and the first shaft hole 151 can directly lubricate the third bearing 168, and the lubricating oil flowing in through the gap between the second rotating shaft 171 and the second bearing 172 can directly lubricate the fourth bearing 173, thus achieving a better lubrication effect.

[0085] As an example, combined Figure 4 and Figure 16 As shown, a third opening 155 can also be formed at the second end 115 of the main housing 111. One end of the third opening 155 can extend through to the end face of the second end 115, and the other end of the third opening 155 can communicate with the second shaft hole 152. It is understood that when the second cover 113 is connected to the second end 115, the third opening 155 can also be sealed by the second cover 113. The fourth bearing 173 can be deployed in the third opening 155 and supported by the fourth bearing 173 within the third opening 155. After the lubricating oil flows into the third opening 155 through the gap between the second shaft 171 and the second shaft hole 152, it can directly lubricate the fourth bearing 173.

[0086] In some embodiments, combined with Figure 4 and Figure 16As shown, the first housing 110 may be provided with an oil return hole 153. One end of the oil return hole 153 may extend into the compression chamber 121, and the other end of the oil return hole 153 may communicate with the third bearing chamber 150 to form at least a partial oil return channel. In some examples, one end of the oil return hole 153 may communicate with the first space 128 of the compression chamber 121. This helps to reduce the pressure at one end of the oil return hole 153 and facilitates the return of lubricating oil in the third bearing chamber 150 to the compression chamber 121.

[0087] In some examples, combined Figure 4 and Figure 16 As shown, the oil return channel may further include a second groove 156 formed on the end face of the second end 115, and the second opening 154 and / or the third opening 155 may communicate with the second groove 156, which may communicate with the oil return hole 153. Thus, the lubricating oil in the second opening 154 and / or the third opening 155 can flow into the return hole via the second groove 156. As an example, the other end of the oil return hole 153 may extend above the third opening 155. The second groove 156 may be arc-shaped or approximately arc-shaped, and may extend circumferentially along the third opening 155. The top end of the second groove 156 may communicate with the oil return hole 153, and the bottom end of the second groove 156 may communicate with the second opening 154. It is understood that the form of the second groove 156 is not limited. If there is a gap between the inner surface of the second cover 113 and the end face of the second end 115, the lubricating oil in the second opening 154 and the third opening 155 can also flow into the return hole through the gap between the second cover 113 and the second end 115.

[0088] Figure 17 A cross-sectional view of a compressor according to some embodiments of the present disclosure is shown. See also Figure 17 As shown, the compressor of this disclosure includes a motor 200 and a compressor main unit 100 as described in any of the above embodiments. The first screw 160 of the compressor main unit 100 is a female screw (also referred to as a female rotor), and the second screw 170 of the compressor main unit 100 is a male screw (also referred to as a male rotor). The motor 200 is drivenly connected to the female screw. Thus, a female rotor-driven twin-screw compressor can be formed. During the operation of the twin-screw compressor (especially in the initial stage after startup), lubricating oil is supplied to the compression chamber 121 through the first oil supply channel 181 via the first bearing chamber 130. This helps to reduce the temperature of the male and female rotors near the air inlet, ensuring stable operation of the compressor main unit 100 and improving the stability of the compressor.

[0089] In some embodiments, combined with Figure 17As shown, the motor 200 may include a second housing 210, a stator 220, and a rotor 230. The second housing 210 may be directly connected to the first housing 110, for example, the second housing 210 may be directly connected to the first end 114 of the main housing 111. The stator 220 is fixed inside the second housing 210, and the rotor 230 is accommodated in the hollow inner cavity 221 of the stator 220. One end of the first rotating shaft 161 extends into the second housing 210, and the rotor 230 is deployed on the first rotating shaft 161 of the first screw 160. That is, the motor 200 does not have a separate rotor shaft. The first rotating shaft 161 of the first screw 160 also serves as the rotor shaft of the motor 200. The rotational power generated by the rotor 230 is directly transmitted to the first screw 160 to drive the first screw 160 to rotate. Thus, by deploying the rotor 230 directly on the first rotating shaft 161, the transmission mechanism between the motor 200 and the compressor main unit 100 is eliminated, which is beneficial to improving transmission efficiency, greatly simplifying the structure of the compressor, and reducing the size of the compressor. Of course, the above-described connection method between the motor 200 and the compressor host 100 is merely exemplary. In practical applications, the motor 200 can also be connected to the compressor host 100 through any suitable transmission mechanism, and the embodiments disclosed herein do not impose any limitations on this.

[0090] The various embodiments of this disclosure have been described above. These descriptions are exemplary and not exhaustive, and are not limited to the disclosed embodiments. Many modifications and variations will be apparent to those skilled in the art without departing from the scope and spirit of the described embodiments. The terminology used herein is chosen to best explain the principles, practical application, or technical improvements to the embodiments in the market, or to enable others skilled in the art to understand the embodiments disclosed herein.

Claims

1. A compressor main unit, characterized in that, include: A first housing has an internal compression chamber and a first bearing chamber. The first bearing chamber has a first opening and communicates with one end of the compression chamber through the first opening. A first bearing is disposed in the first bearing chamber. The first opening is configured to expose at least a portion of the first bearing in the compression chamber. The first screw and the second screw are both deployed in the compression chamber and mesh with each other. One end of the first shaft of the first screw extends into the first bearing chamber through the first opening and is supported by the first bearing to rotate. as well as A first oil supply channel is disposed within the first housing, one end of the first oil supply channel communicating with the first bearing chamber to provide lubricating oil to the first bearing chamber, such that the lubricating oil flows into the compression chamber via the first bearing exposed in at least a portion of the compression chamber.

2. The compressor main unit according to claim 1, characterized in that, The first opening has a flange extending radially inward along the first axis of rotation. The flange is located on the side of the first bearing near the compression chamber and supports the first bearing. The flange is configured to define a fluid passage between the compression chamber and the first bearing chamber, so that at least a portion of the first bearing is exposed in the compression chamber.

3. The compressor main unit according to claim 2, characterized in that, At least a portion of the first bearing is not covered by the projection of the flange in the axial direction of the first shaft to form the fluid channel.

4. The compressor main unit according to claim 3, characterized in that, The flange includes a first portion that extends circumferentially along the first opening and is partially annular.

5. The compressor main unit according to claim 4, characterized in that, The first portion extends radially inward by a first distance, and the outer circumference of the outer ring of the first bearing and the outer circumference of the inner ring have a second distance in the radial direction, the first distance being greater than or equal to the second distance.

6. The compressor main unit according to claim 4, characterized in that, A three-dimensional sealing line is provided between the first screw and the second screw, and the projection of the three-dimensional sealing line on the axial direction of the first rotating shaft falls entirely or partially within the first part.

7. The compressor main unit according to claim 4, characterized in that, The first housing also has a second bearing chamber located near the first bearing chamber and communicating with the compression chamber. The second bearing chamber contains a second bearing and a bearing seat. One end of the second shaft of the second screw extends into the second bearing chamber and is supported and rotated by the second bearing. The bearing seat is located on the side of the second bearing near the compression chamber, and the projection of the bearing seat on the axial direction of the second shaft covers the second bearing to limit the second bearing from being exposed in the compression chamber.

8. The compressor main unit according to claim 7, characterized in that, There is a three-dimensional sealing line between the first screw and the second screw, and the projection of the three-dimensional sealing line on the axial direction of the first rotating shaft falls entirely into the first part and the bearing seat.

9. The compressor main unit according to claim 4, characterized in that, The first housing is provided with a radial air inlet that communicates with one end of the compression chamber, and the radial air inlet is close to the first bearing chamber.

10. The compressor main unit according to claim 9, characterized in that, The first screw has a radial air inlet closure line corresponding to the radial air inlet, the radial air inlet closure line including an end point near the first opening, the projection of the end point in the axial direction of the first shaft falling into the first portion.

11. The compressor main unit according to claim 4, characterized in that, The flange also includes a second portion that extends circumferentially along the first opening and is partially annular.

12. The compressor main unit according to claim 11, characterized in that, The first portion extends radially inward by a first distance, and there is a second radial distance between the outer circumference of the outer ring and the outer circumference of the inner ring of the first bearing. The second portion extends radially inward by a third distance, and the third distance is less than the first distance. The second distance is less than or equal to the first distance, and the third distance is less than the second distance.

13. The compressor main unit according to claim 11, characterized in that, The angle at which the first portion extends circumferentially from the first opening falls within the range of 45° to 300°, and / or The sum of the angle at which the first portion extends circumferentially in the first opening and the angle at which the second portion extends circumferentially in the first opening is 360°.

14. The compressor main unit according to any one of claims 1-13, characterized in that, The first bearing has a gap extending through both ends of the first bearing so that lubricating oil supplied to the first bearing housing flows into the compression chamber through the gap.

15. The compressor main unit according to any one of claims 1-13, characterized in that, The first oil supply channel is disposed within the first housing along the axial direction of the first rotating shaft, and the other end of the first oil supply channel is located at the axial center of the first housing to facilitate the introduction of lubricating oil from the outside.

16. The compressor main unit according to any one of claims 1-13, characterized in that, The first housing is further provided with at least one oil inlet, the at least one oil inlet being located near the axial center of the first screw and / or the second screw; and The first housing is further provided with a second oil supply channel, which is connected to the other end of the first oil supply channel and the at least one oil inlet, so as to provide lubricating oil to the first oil supply channel and to provide lubricating oil to the compression chamber via the at least one oil inlet.

17. The compressor main unit according to any one of claims 1-13, characterized in that, The first bearing housing is also equipped with a dynamic seal component fitted onto the first rotating shaft. The first bearing is close to the compression chamber, and the dynamic seal component is far from the compression chamber. The first oil supply channel is adapted to deliver lubricating oil between the first bearing and the dynamic seal component.

18. The compressor main unit according to any one of claims 1-13, characterized in that, The first housing includes at least a main housing and a first cover. The main housing has a compression chamber and a first opening inside. The first opening extends to the end face of a first end of the main housing, and one end of the first oil supply channel extends to the end face of the first end. The first cover is connected to the first end to seal the first opening. as well as The end face of the first end and / or the surface of the first cover opposite to the end face are provided with a first groove suitable for connecting the first opening and the first oil supply channel.

19. The compressor main unit according to claim 18, characterized in that, The first groove is sized such that the flow rate of lubricating oil supplied to the compression chamber through the first oil supply channel accounts for 5%-20% of the total flow rate of lubricating oil supplied to the compression chamber.

20. The compressor main unit according to any one of claims 1-13, characterized in that, The first housing is also provided with an exhaust port that communicates with the other end of the compression chamber, and the interior of the first housing is also provided with a third bearing chamber near the exhaust port; The third bearing chamber is provided with a third bearing and a fourth bearing. The third bearing is used to support the other end of the first rotating shaft that extends into the third bearing chamber, and the fourth bearing is used to support the other end of the second rotating shaft of the second screw that extends into the third bearing chamber.

21. The compressor main unit according to claim 20, characterized in that, The compression chamber is connected to the third bearing chamber via an oil supply channel and an oil return channel, respectively, to be adapted to supply lubricating oil to the third bearing chamber via the oil supply channel, and to receive lubricating oil returning from the third bearing chamber via the oil return channel.

22. The compressor main unit according to claim 21, characterized in that, The compression chamber communicates with the third bearing chamber through a first shaft hole, and the other end of the first rotating shaft extends into the third bearing chamber through the first shaft hole. A gap exists between the first rotating shaft and the first shaft hole to form at least a portion of the oil delivery channel, and / or The compression chamber is connected to the third bearing chamber through the second shaft hole, and the other end of the second shaft extends into the third bearing chamber through the second shaft hole. There is a gap between the second shaft and the second shaft hole to form at least part of the oil delivery channel.

23. The compressor main unit according to claim 21, characterized in that, The first housing has an oil return hole with one end extending into the compression chamber, and the other end of the oil return hole is connected to the third bearing chamber to form at least part of the oil return channel.

24. The compressor main unit according to claim 23, characterized in that, The first housing includes a main housing with the compression chamber inside and a second cover connected to a second end of the main housing; The second end has a second opening adapted to accommodate the third bearing and / or a third opening adapted to accommodate the fourth bearing, the second opening and / or the third opening forming at least a portion of the third bearing chamber; and The other end of the oil return hole extends through to the end face of the second end; the oil return channel also includes a second groove formed on the end face of the second end, the second groove communicating with the second opening and / or the third opening, and the oil return hole communicating with the second groove.

25. A compressor, characterized in that, The compressor includes a motor and a compressor main unit as described in any one of claims 1 to 24, wherein the first screw of the compressor main unit is a female screw, the second screw of the compressor main unit is a male screw, and the motor is drivenly connected to the female screw.

26. The compressor according to claim 25, characterized in that, The motor includes a second housing, a stator, and a rotor. The stator is fixed inside the second housing, and the rotor is housed in the hollow cavity of the stator. One end of the first shaft of the first screw extends into the second housing, and the rotor is deployed on the first shaft of the first screw. The second housing is directly connected to the first housing.

Images