Air cylinder assembly and compressor

Abstract

The invention relates to the technical field of compressors, and discloses an air cylinder assembly and a compressor. The air cylinder assembly comprises a first air cylinder, a second air cylinder and a flow dividing channel. The first cylinder includes an intake passage having an intake port and an exhaust port. The second air cylinder and the first air cylinder are coaxially arranged. The shunting channel is arranged on the first cylinder and the second cylinder. One end of the shunting channel is a shunting inlet and is communicated with the air inlet channel, and the other end of the shunting channel is a shunting outlet and is positioned on the inner wall of the second cylinder. The axial size of the first air cylinder is larger than that of the second air cylinder. Air enters the air inlet channel through the air suction port and then is shunted, enters the first air cylinder through the air outlet and enters the second air cylinder through the shunting channel. According to the compressor, the axial size of the first air cylinder is larger than that of the second air cylinder, the diameter of the air suction port can be increased, the air inlet sectional area can be increased, the air suction amount during high-frequency operation of the compressor is improved, and the air suction efficiency is improved.

Description

Technical Field

[0001] The present application relates to the technical field of compressors, for example, to a cylinder assembly and a compressor. Background Art

[0002] At present, it has become a trend to design a two-cylinder rotor compressor with a liquid reservoir connected to two intake pipes as a liquid reservoir connected to one intake pipe in order to reduce the cost of the compressor.

[0003] In the related art, a twin-cylinder rotor compressor includes a liquid accumulator, an upper cylinder and a lower cylinder, wherein the cylinder height of the upper cylinder is equal to the cylinder height of the lower cylinder, that is, the axial dimension of the upper cylinder is equal to the axial dimension of the lower cylinder. The liquid accumulator is connected to the upper cylinder through an air intake pipe, and the gas enters the upper cylinder from the air intake pipe and is diverted to the lower cylinder.

[0004] In the process of implementing the embodiments of the present disclosure, it is found that there are at least the following problems in the related art:

[0005] In the related art, in the case where the sum of the axial dimensions of the upper cylinder and the lower cylinder is constant, the axial dimensions of the upper cylinder are equal to the axial dimensions of the lower cylinder, and the axial dimensions of the upper cylinder limit the diameter of the air intake port of the upper cylinder, resulting in the inability to increase the intake cross-sectional area, causing the compressor to have insufficient air intake when operating at high frequency, and increasing the air intake flow rate. The increase in the air intake flow rate also increases the flow resistance and pulsation, and reduces the air intake efficiency.

[0006] Moreover, when the axial dimensions of the upper cylinder and the lower cylinder are equal, in order to make the lower cylinder outlet evenly deliver air to the lower cylinder cavity, the stroke from the upper cylinder air intake to the lower cylinder outlet is made larger. And the angle between the air intake channel of the upper cylinder and the flow diversion channel of the lower cylinder is limited and cannot be increased, resulting in greater flow resistance and decreased energy efficiency of the compressor as the power increases.

[0007] It should be noted that the information disclosed in the above background technology section is only used to enhance the understanding of the background of the present application, and therefore may include information that does not constitute the prior art known to ordinary technicians in the field. Summary of the invention

[0008] In order to provide a basic understanding of some aspects of the disclosed embodiments, a brief summary is given below. The summary is not an extensive review, nor is it intended to identify key / critical components or delineate the scope of protection of these embodiments, but rather serves as a prelude to the detailed description that follows.

[0009] The embodiments of the present disclosure provide a cylinder assembly and a compressor to increase the air intake volume when the compressor is running at a high frequency, improve the air intake efficiency, and reduce the gas flow resistance.

[0010] In some embodiments, a cylinder assembly is provided, including: a first cylinder, the first cylinder including an intake passage having an intake port and an outlet port; a second cylinder, coaxially arranged with the first cylinder; a diversion passage, opened between the first cylinder and the second cylinder; one end of the diversion passage is a diversion inlet and is connected to the intake passage, and the other end of the diversion passage is a diversion outlet and is located on the inner wall of the second cylinder; wherein the axial dimension of the first cylinder is greater than the axial dimension of the second cylinder; the gas enters the intake passage through the intake port and is diverted, entering the first cylinder through the outlet port and entering the second cylinder through the diversion passage.

[0011] Optionally, along the direction from the air intake port to the air outlet port, the air intake passage is inclined toward a direction close to the second cylinder.

[0012] Optionally, the first cylinder further includes: a flared portion, which is arranged at the air outlet end of the air inlet passage and is located on a side away from the second cylinder; and the flared portion is connected with the air outlet to form an expanded air outlet.

[0013] Optionally, the distance from the upper edge point of the expanded air outlet to the upper end of the first cylinder is equal to the distance from the lower edge point of the expanded air outlet to the lower end of the first cylinder.

[0014] Optionally, the distance from the upper edge of the expanded air outlet to the upper end of the first cylinder and the distance from the lower edge of the expanded air outlet to the lower end of the first cylinder are both L, and satisfy L≥1mm.

[0015] Optionally, on an axial cross section of the first cylinder passing through an upper edge point of the expanded air outlet, an angle between an upper edge line of the expanded portion and a radial line of the cylinder is θ.

[0016] Optionally, 30°≤θ≤60°.

[0017] Optionally, the axial dimension H1 of the first cylinder and the axial dimension H2 of the second cylinder satisfy:

[0018] H2

[0019] Optionally, the angle β between the axis of the air inlet channel and the axis of the flow diversion channel satisfies:

[0020] 90°≤β<165°.

[0021] Optionally, the cylinder assembly further includes: a partition plate, disposed between the first cylinder and the second cylinder; and the diversion channel passes through the partition plate.

[0022] Optionally, an axial dimension T of the partition satisfies: T≤H2.

[0023] ​Optionally, the diversion channel includes: a first diversion channel, opened in the first cylinder; a second diversion channel, opened in the partition; a third diversion channel, opened in the second cylinder; wherein the first diversion channel, the second diversion channel and the third diversion channel are connected in sequence, the end of the first diversion channel away from the second diversion channel is a diversion inlet, and the end of the third diversion channel away from the second diversion channel is a diversion outlet.

[0024] Optionally, the axis of the first diverter channel, the axis of the second diverter channel and the axis of the third diverter channel are located in the same straight line or are not located in the same straight line; when the axis of the first diverter channel, the axis of the second diverter channel and the axis of the third diverter channel are not located in the same straight line, the angle between the axis of the first diverter channel and the axis of the intake channel is smaller than the angle between the axis of the second diverter channel and the axis of the intake channel, and the angle between the axis of the second diverter channel and the axis of the intake channel is smaller than the angle between the axis of the third diverter channel and the axis of the intake channel.

[0025] Optionally, when the axis of the first diversion channel, the axis of the second diversion channel and the axis of the third diversion channel are located in the same straight line, the angle β between the straight line passing through the axis of the first diversion channel, the axis of the second diversion channel and the axis of the third diversion channel and the axis of the intake channel satisfies: 90°≤β<165°.

[0026] Optionally, the angle β1 between the straight line passing through the axis of the first flow diversion channel and the axis of the air intake channel, the angle β2 between the straight line passing through the axis of the second flow diversion channel and the axis of the air intake channel, and the angle β3 between the straight line passing through the axis of the third flow diversion channel and the axis of the air intake channel satisfy the following relationship:

[0027] 90°≤β1<β2<β3<165°.

[0028] In some embodiments, a compressor is provided, comprising: a cylinder assembly as described above; a liquid reservoir; an intake bend pipe, one end of which is connected to the outlet of the liquid reservoir, and the other end is connected to the air intake port of the intake channel of the cylinder assembly; when the intake channel is inclined toward a direction close to the second cylinder along the direction from the air intake port to the air outlet, the bend angle of the intake bend pipe is greater than 90°.

[0029] Optionally, the compressor comprises a twin-cylinder rotary compressor.

[0030] Optionally, the intake elbow comprises a first pipe and a second pipe connected to each other. The first pipe is connected to the outlet of the liquid reservoir. The second pipe is connected to the air intake of the intake channel of the cylinder assembly. The first pipe is arranged vertically. The angle between the first pipe and the second pipe is greater than 90°.

[0031] The cylinder assembly and compressor provided by the embodiments of the present disclosure can achieve the following technical effects:

[0032] The cylinder assembly provided in the embodiment of the present disclosure can increase the diameter of the intake port, increase the intake cross-sectional area, increase the intake volume when the compressor is running at a high frequency, and improve the intake efficiency by making the axial dimension of the first cylinder larger than the axial dimension of the second cylinder when the sum of the axial dimension of the first cylinder and the axial dimension of the second cylinder is constant.

[0033] Moreover, by making the axial dimension of the first cylinder larger than that of the second cylinder, uniform air delivery from the diverter outlet to the second cylinder is achieved, while the stroke from the air intake port of the first cylinder to the diverter outlet of the second cylinder is reduced, the angle between the axis of the air intake passage and the axis of the diverter passage is increased, the gas flow resistance is reduced, and the energy efficiency of the compressor is improved.

[0034] The above general description and the following description are exemplary and explanatory only and are not intended to limit the present application. BRIEF DESCRIPTION OF THE DRAWINGS

[0035] One or more embodiments are exemplarily described by corresponding drawings, which do not limit the embodiments. Elements with the same reference numerals in the drawings are shown as similar elements, and the drawings do not constitute a scale limitation, and wherein:

[0036] Figure 1 is a cross-sectional schematic diagram of a compressor provided by an embodiment of the present disclosure;

[0037] Figure 2 yes Figure 1 Partial schematic diagram of the compressor shown Figure 1 ;

[0038] Figure 3 yes Figure 1 Partial schematic diagram of the compressor shown Figure 2 ;

[0039] Figure 4 is a cross-sectional schematic diagram of a compressor provided by another embodiment of the present disclosure;

[0040] Figure 5 yes Figure 4 A partial schematic diagram of the compressor shown;

[0041] Figure 6 This is a comparison chart of low-temperature heating capacity when the compressor operates at 90Hz;

[0042] Figure 7 This is a comparison chart of low-temperature heating capacity when the compressor operates at a frequency of 120 Hz.

[0043] Reference numerals:

[0044] 100: Cylinder assembly;

[0045] 200: first cylinder; 201: air intake passage; 2011: air intake port; 2012: air outlet port; 202: expansion portion;

[0046] 300: second cylinder;

[0047] 400: diversion channel; 401: first diversion channel; 402: second diversion channel; 403: third diversion channel;

[0048] 500: partition;

[0049] 600: compressor; 601: liquid reservoir; 602: air intake elbow. DETAILED DESCRIPTION

[0050] In order to be able to understand the features and technical contents of the embodiments of the present disclosure in more detail, the implementation of the embodiments of the present disclosure is described in detail below in conjunction with the accompanying drawings. The attached drawings are for reference only and are not used to limit the embodiments of the present disclosure. In the following technical description, for the convenience of explanation, a full understanding of the disclosed embodiments is provided through multiple details. However, one or more embodiments can still be implemented without these details. In other cases, to simplify the drawings, well-known structures and devices can be simplified for display.

[0051] The terms "first", "second", etc. in the specification and claims of the embodiments of the present disclosure and the above-mentioned drawings are used to distinguish similar objects, and are not necessarily used to describe a specific order or sequence. It should be understood that the terms used in this way can be interchanged where appropriate, so as to describe the embodiments of the embodiments of the present disclosure described herein. In addition, the terms "including" and "having" and any variations thereof are intended to cover non-exclusive inclusions.

[0052] In the embodiments of the present disclosure, the terms "upper", "lower", "inside", "middle", "outside", "front", "back" and the like indicate directions or positional relationships based on the directions or positional relationships shown in the accompanying drawings. These terms are mainly intended to better describe the embodiments of the present disclosure and their embodiments, and are not intended to limit the indicated devices, elements or components to have a specific direction, or to be constructed and operated in a specific direction. Moreover, in addition to being used to indicate directions or positional relationships, some of the above terms may also be used to indicate other meanings. For example, the term "upper" may also be used to indicate a certain dependency or connection relationship in certain circumstances. For those of ordinary skill in the art, the specific meanings of these terms in the embodiments of the present disclosure can be understood according to specific circumstances.

[0053] In addition, the terms "disposed", "connected", and "fixed" should be understood in a broad sense. For example, "connected" can be a fixed connection, a detachable connection, or an integral structure; it can be a mechanical connection, or an electrical connection; it can be a direct connection, or an indirect connection through an intermediate medium, or it can be an internal connection between two devices, elements, or components. For those of ordinary skill in the art, the specific meanings of the above terms in the embodiments of the present disclosure can be understood according to specific circumstances.

[0054] Unless otherwise stated, the term "plurality" means two or more.

[0055] It should be noted that, in the absence of conflict, the embodiments and features in the embodiments of the present disclosure may be combined with each other.

[0056] Combination Figures 1 to 7 As shown, an embodiment of the present disclosure provides a cylinder assembly 100. The cylinder assembly 100 includes a first cylinder 200, a second cylinder 300 and a diverter channel 400. The first cylinder 200 includes an intake channel 201 having an intake port 2011 and an outlet port 2012. The second cylinder 300 is coaxially arranged with the first cylinder 200. The diverter channel 400 is opened in the first cylinder 200 and the second cylinder 300. One end of the diverter channel 400 is a diverter inlet and is connected to the intake channel 201, and the other end of the diverter channel 400 is a diverter outlet and is located on the inner wall of the second cylinder 300. Among them, the axial dimension of the first cylinder 200 is greater than the axial dimension of the second cylinder 300. The gas enters the intake channel 201 through the intake port 2011 and then is diverted, enters the first cylinder 200 through the outlet port 2012, and enters the second cylinder 300 through the diverter channel 400.

[0057] The cylinder assembly 100 provided in the embodiment of the present disclosure can increase the diameter of the intake port 2011 and the intake cross-sectional area, increase the intake volume when the compressor 600 is running at a high frequency, and improve the intake efficiency by making the axial dimension of the first cylinder 200 larger than the axial dimension of the second cylinder 300 when the sum of the cylinder height of the first cylinder 200 and the cylinder height of the second cylinder 300 is constant.

[0058] The cylinder assembly 100 provided in the embodiment of the present disclosure has an axial dimension of the first cylinder 200 that is larger than the axial dimension of the second cylinder 300. While achieving uniform air delivery from the diversion outlet to the second cylinder 300, the stroke from the air intake port 2011 of the first cylinder 200 to the diversion outlet of the second cylinder 300 is reduced, the angle between the axis of the intake channel 201 and the axis of the diversion channel 400 is increased, the gas flow resistance is reduced, and the energy efficiency of the compressor 600 is improved.

[0059] Specifically, the diversion outlet is located in the middle of the inner wall of the second cylinder 300. The diversion outlet is not arranged at the upper or lower part of the inner wall of the second cylinder 300, so that the diversion outlet can evenly deliver gas to the middle of the second cylinder 300, thereby evenly delivering gas to the second cylinder 300.

[0060] Compared with the case in the related art where the cylinder height of the upper cylinder is equal to that of the lower cylinder, this embodiment allows the split outlet to evenly deliver gas to the second cylinder 300. By making the axial dimension of the second cylinder 300 smaller than the axial dimension of the first cylinder 200, the stroke from the air intake port 2011 of the first cylinder 200 to the split outlet of the second cylinder 300 can be reduced, the angle between the axis of the air intake channel 201 and the axis of the split channel 400 can be increased, and the gas flow resistance can be reduced.

[0061] Combination Figures 1 to 5 As shown, in some embodiments, along the direction from the air intake port 2011 to the air outlet port 2012 , the air intake passage 201 is inclined toward the direction close to the second cylinder 300 .

[0062] In this embodiment, the intake channel 201 is tilted so that the gas sucked into the intake channel 201 can be more easily diverted to the diversion channel 400, and the gas sucked into the air intake port 2011 of the first cylinder 200 can be more smoothly diverted to the second cylinder 300, thereby reducing the gas flow resistance.

[0063] Combination Figures 1 to 5 As shown, in some embodiments, the first cylinder 200 further includes a flared portion 202. The flared portion 202 is disposed at the end of the air outlet 2012 of the air inlet passage 201 and is located on a side away from the second cylinder 300. The flared portion 202 and the air outlet 2012 are connected to form an expanded air outlet 2012.

[0064] In this embodiment, when the intake passage 201 is inclined toward the second cylinder 300 , by providing a flared portion 202 at the outlet 2012 end of the intake passage 201 , local eddy current losses can be reduced and uniform air delivery into the first cylinder 200 can be achieved.

[0065] Combination Figure 2 As shown, in some embodiments, the distance from the upper edge of the expanded air outlet 2012 to the upper end of the first cylinder 200 is equal to the distance from the lower edge of the expanded air outlet 2012 to the lower end of the first cylinder 200 .

[0066] In this embodiment, by providing the flared portion 202, the distance from the upper edge of the expanded gas outlet 2012 to the upper end of the first cylinder 200 is equal to the distance from the lower edge of the expanded gas outlet 2012 to the lower end of the first cylinder 200. Thus, the gas sucked in by the air inlet 2011 of the first cylinder 200 is evenly delivered into the compression chamber of the first cylinder 200 through the expanded gas outlet 2012.

[0067] Specifically, since the air intake passage 201 is inclined toward the direction close to the second cylinder 300, the gas sucked into the air intake port 2011 is located at the lower position in the compression chamber when entering the compression chamber of the first cylinder 200 through the air intake passage 201. By setting the flaring portion 202, the distance from the upper edge point of the expanded air outlet 2012 to the upper end of the first cylinder 200 is equal to the distance from the lower edge point of the expanded air outlet 2012 to the lower end of the first cylinder 200, thereby making the gas sent into the compression chamber of the first cylinder 200 located in the middle position in the compression chamber, so as to improve the uniformity of air delivery.

[0068] Furthermore, in this embodiment, the flared portion 202 is provided to increase the gas supply cross-sectional area so as to reduce the gas flow rate, thereby reducing the gas flow pulsation and also reducing the local eddy loss.

[0069] Combination Figure 2 As shown, optionally, the distance from the upper edge of the expanded air outlet 2012 to the upper end of the first cylinder 200 and the distance from the lower edge of the expanded air outlet 2012 to the lower end of the first cylinder 200 are both L, and satisfy L≥1mm.

[0070] In this embodiment, by setting L≥1 mm, the gas can enter the compression chamber of the first cylinder 200 evenly, and at the same time, the strength and working reliability of the first cylinder 200 can be improved.

[0071] Combination Figure 2 As shown, optionally, on the axial cross section of the first cylinder 200 passing the upper edge point of the expanded gas outlet 2012, the angle between the upper edge line of the expanded portion 202 and the radial line of the cylinder is θ.

[0072] Optionally, 30°≤θ≤60°.

[0073] In this embodiment, 30°≤θ≤60° is adopted to achieve that the distance from the upper edge point of the expanded air outlet 2012 to the upper end of the first cylinder 200 is equal to the distance from the lower edge point of the expanded air outlet 2012 to the lower end of the first cylinder 200 .

[0074] Combination Figures 1 to 5 As shown, in some embodiments, the axial dimension H1 of the first cylinder 200 and the axial dimension H2 of the second cylinder 300 satisfy:

[0075] H2

[0076] In this embodiment, when the sum of the axial dimension H1 of the first cylinder 200 and the axial dimension H2 of the second cylinder 300 is constant, H2

[0077] Exemplary, combined Figure 6 As shown, when the cylinder assembly 100 is applied to the compressor 600, the low-temperature heating capacity of the compressor 600 is verified by taking the operating frequency of the compressor 600 as 90Hz as an example. When the sum of the axial dimension H1 of the first cylinder 200 and the axial dimension H2 of the second cylinder 300 is constant, the low-temperature heating capacity (unit: W) of the compressor 600 is tested in four cases of H1=H2, H1=1.2H2, H1=1.5H2, and H1=1.8H2. The test results are: when H1=H2, the low-temperature heating capacity of the compressor 600 is 10968W; when H1=1.2H2, the low-temperature heating capacity of the compressor 600 is 11135W; when H1=1.5H2, the low-temperature heating capacity of the compressor 600 is 11153W; when H1=1.8H2, the low-temperature heating capacity of the compressor 600 is 11038W. It can be obtained that the low-temperature heating capacity of the compressor 600 in the three cases of H1=1.2H2, H1=1.5H2, and H1=1.8H2 is greater than the low-temperature heating capacity of the compressor 600 in the case of H1=H2. Therefore, when the sum of the axial dimension H1 of the first cylinder 200 and the axial dimension H2 of the second cylinder 300 is constant, the low-temperature heating capacity of the compressor 600 can be increased by making the axial dimension H1 of the first cylinder 200 greater than the axial dimension H2 of the second cylinder 300.

[0078] Exemplary, combined Figure 7 ​​As shown, when the cylinder assembly 100 is applied to the compressor 600, the effect of the low-temperature heating capacity of the compressor 600 is verified by taking the operating frequency of the compressor 600 as 120Hz as an example. When the sum of the axial dimension H1 of the first cylinder 200 and the axial dimension H2 of the second cylinder 300 is constant, the low-temperature heating capacity (unit: W) of the compressor 600 is tested in four cases of H1=H2, H1=1.2H2, H1=1.5H2, and H1=1.8H2. The test results are: when H1=H2, the low-temperature heating capacity of the compressor 600 is 14624W; when H1=1.2H2, the low-temperature heating capacity of the compressor 600 is 14846W; when H1=1.5H2, the low-temperature heating capacity of the compressor 600 is 14870W; when H1=1.8H2, the low-temperature heating capacity of the compressor 600 is 14717W. It can be obtained that the low-temperature heating capacity of the compressor 600 in the three cases of H1=1.2H2, H1=1.5H2, and H1=1.8H2 is greater than the low-temperature heating capacity of the compressor 600 in the case of H1=H2. Therefore, when the sum of the axial dimension H1 of the first cylinder 200 and the axial dimension H2 of the second cylinder 300 is constant, the low-temperature heating capacity of the compressor 600 can be increased by making the axial dimension H1 of the first cylinder 200 greater than the axial dimension H2 of the second cylinder 300.

[0079] Combination Figures 1 to 5 As shown, in some embodiments, the angle β between the axis of the air inlet channel 201 and the axis of the flow diversion channel 400 satisfies:

[0080] 90°≤β<165°.

[0081] In this embodiment, by setting 90°≤β<165°, the fluid resistance can be reduced and the energy efficiency of the compressor 600 can be improved.

[0082] Exemplary, combined Figure 3As shown, the angle β between the axis of the air intake channel 201 and the axis of the flow diversion channel 400 is related to the horizontal distance A from the center of the flow diversion inlet to the inner wall of the first cylinder 200 and the vertical distance B from the center of the flow diversion inlet to the center of the flow diversion outlet. In actual application, the value of the horizontal distance A from the center of the flow diversion inlet to the inside of the first cylinder 200 is fixed. The smaller the vertical distance B from the center of the flow diversion inlet to the center of the flow diversion outlet, the larger the angle β between the axis of the air intake channel 201 and the axis of the flow diversion channel 400. The vertical distance B from the center of the flow diversion inlet to the center of the flow diversion outlet is related to the distance L from the lower edge point of the expansion outlet 2012 to the lower end of the first cylinder 200, the axial dimension T of the partition 500, and the distance from the center of the flow diversion outlet to the upper end of the second cylinder 300. In actual application, the distance L from the lower edge point of the expansion outlet 2012 to the lower end of the first cylinder 200 and the axial dimension T of the partition 500 are both the minimum values ​​within the allowable range. Therefore, when the sum of the axial dimension H1 of the first cylinder 200 and the axial dimension H2 of the second cylinder 300 is constant and uniform air delivery is achieved, by reducing the axial dimension H2 of the second cylinder 300, the distance from the center of the diverter outlet to the upper end of the second cylinder 300 can be reduced, thereby reducing the vertical distance B from the center of the diverter inlet to the center of the diverter outlet, and increasing the angle β between the axis of the intake channel 201 and the axis of the diverter channel 400, thereby reducing the fluid resistance and improving the energy efficiency of the compressor 600.

[0083] Combination Figures 1 to 5 As shown, in some embodiments, the cylinder assembly 100 further includes a partition plate 500. The partition plate 500 is disposed between the first cylinder 200 and the second cylinder 300. The flow dividing channel 400 passes through the partition plate 500.

[0084] In this embodiment, the partition plate 500 and the flow dividing channel 400 passing through the partition plate 500 are provided so as to ensure the stable operation of the cylinder assembly 100 .

[0085] Optionally, the axial dimension T of the partition 500 satisfies:

[0086] T≤H2.

[0087] Combination Figures 1 to 5 As shown, in some embodiments, the flow diversion channel 400 includes a first flow diversion channel 401, a second flow diversion channel 402, and a third flow diversion channel 403. The first flow diversion channel 401 is opened in the first cylinder 200. The second flow diversion channel 402 is opened in the partition 500. The third flow diversion channel 403 is opened in the second cylinder 300. Among them, the first flow diversion channel 401, the second flow diversion channel 402, and the third flow diversion channel 403 are connected in sequence. One end of the first flow diversion channel 401 away from the second flow diversion channel 402 is a flow diversion inlet. One end of the third flow diversion channel 403 away from the second flow diversion channel 402 is a flow diversion outlet.

[0088] In this embodiment, by opening a first diversion channel 401 in the first cylinder 200, opening a second diversion channel 402 in the partition 500, and opening a third diversion channel 403 in the second cylinder 300, and connecting the first diversion channel 401, the second diversion channel 402 and the third diversion channel 403 in sequence, the gas sucked into the intake channel 201 enters the second cylinder 300 through the diversion channel 400, thereby realizing the smooth operation of the second cylinder 300.

[0089] Combination Figures 1 to 3 As shown, in some embodiments, the axis of the first diversion channel 401, the axis of the second diversion channel 402, and the axis of the third diversion channel 403 are located in the same straight line.

[0090] In this embodiment, the axes of the first flow diversion channel 401 , the second flow diversion channel 402 and the third flow diversion channel 403 are located in the same straight line, so that the gas sucked into the intake channel 201 can smoothly enter the second cylinder 300 .

[0091] Optionally, an angle β between a straight line passing through the axis of the first diverter channel 401 , the axis of the second diverter channel 402 , and the axis of the third diverter channel 403 and the axis of the air inlet channel 201 satisfies: 90°≤β<165°.

[0092] For example, when the sum of the axial dimension H1 of the first cylinder 200 and the axial dimension H2 of the second cylinder 300 is constant, the angle β (unit: °) between the axis of the intake passage 201 and the axis of the bypass passage 400, the diameter of the intake port 2011 (unit: mm), and the cross-sectional area of ​​the intake port 2011 (unit: mm) in the four cases of H1=H2, H1=1.2H2, H1=1.5H2, and H1=1.8H2 are 2 ) and air inlet 2011 cross-sectional area / compressor 600 displacement (mm 2 / cm 3 ), as shown in Table 1. According to Table 1, it can be seen that the cross-sectional area of ​​the air inlet 2011 / displacement of the compressor 600 in the three cases of H1=1.2H2, H1=1.5H2, and H1=1.8H2 are all greater than the cross-sectional area of ​​the air inlet 2011 / displacement of the compressor 600 in the case of H1=H2. Therefore, when the sum of the axial dimension H1 of the first cylinder 200 and the axial dimension H2 of the second cylinder 300 is constant, the air intake volume of the compressor 600 can be increased by making the axial dimension H1 of the first cylinder 200 greater than the axial dimension H2 of the second cylinder 300.

[0093] Table 1

[0094]

[0095] Combination Figure 4 and Figure 5 As shown, in some embodiments, the axis of the first flow diversion channel 401, the axis of the second flow diversion channel 402, and the axis of the third flow diversion channel 403 are not located in the same straight line. In the case where the axis of the first flow diversion channel 401, the axis of the second flow diversion channel 402, and the axis of the third flow diversion channel 403 are not located in the same straight line, the angle between the axis of the first flow diversion channel 401 and the axis of the air inlet channel 201 is smaller than the angle between the axis of the second flow diversion channel 402 and the axis of the air inlet channel 201. And the angle between the axis of the second flow diversion channel 402 and the axis of the air inlet channel 201 is smaller than the angle between the axis of the third flow diversion channel 403 and the axis of the air inlet channel 201.

[0096] In the present embodiment, the axis of the first diverter channel 401, the axis of the second diverter channel 402 and the axis of the third diverter channel 403 are not located in the same straight line, and the angles between the axis of the first diverter channel 401, the axis of the second diverter channel 402 and the axis of the third diverter channel 403 and the axis of the intake channel 201 gradually increase, so that the gas sucked into the intake channel 201 can enter the second cylinder 300 more smoothly, and then the gas path entering the compression chamber of the second cylinder 300 is smoother, thereby improving the working performance of the cylinder assembly 100.

[0097] Combination Figure 4 and Figure 5 As shown, optionally, the angle β1 between the straight line passing through the axis of the first branch channel 401 and the axis of the air inlet channel 201, the angle β2 between the straight line passing through the axis of the second branch channel 402 and the axis of the air inlet channel 201, and the angle β3 between the straight line passing through the axis of the third branch channel 403 and the axis of the air inlet channel 201 satisfy the following relationship:

[0098] 90°≤β1<β2<β3<165°.

[0099] It can be understood that the ends of the first diversion channel 401 and the second diversion channel 402 are equal in size and structure, and the ends of the second diversion channel 402 and the third diversion channel 403 are equal in size and structure, so as to improve the continuity of gas flow in the diversion channel 400 and reduce flow resistance.

[0100] It is understood that the radial cross-sectional shapes of the first flow diversion channel 401, the second flow diversion channel 402 and the third flow diversion channel 403 are not limited and can be set as required. For example, the radial cross-sectional shapes of the first flow diversion channel 401, the second flow diversion channel 402 and the third flow diversion channel 403 are circular, elliptical, etc.

[0101] Combination Figures 1 to 7As shown, the embodiment of the present disclosure further provides a compressor 600. The compressor 600 includes the aforementioned cylinder assembly 100, a liquid reservoir 601, and an intake elbow 602. One end of the intake elbow 602 is connected to the outlet of the liquid reservoir 601, and the other end of the intake elbow 602 is connected to the air intake port 2011 of the intake channel 201 of the cylinder assembly 100. When the intake channel 201 is inclined toward the direction close to the second cylinder 300 along the direction from the air intake port 2011 to the air outlet 2012, the bend angle ɑ of the intake elbow 602 is greater than 90°.

[0102] In this embodiment, the other end of the intake elbow 602 can extend into the intake channel 201 of the first cylinder 200. After entering the intake channel 201, the gas is split and enters the first cylinder 200 through the gas outlet 2012, and enters the second cylinder 300 through the split channel 400. The axial dimension of the first cylinder 200 connected to the intake elbow 602 of the liquid reservoir 601 is larger than the axial dimension of the second cylinder 300, that is, the cylinder height of the first cylinder 200 is higher than the cylinder height of the second cylinder 300, which is conducive to increasing the diameter of the suction port 2011 to meet the suction volume requirement of the compressor 600.

[0103] In this embodiment, when the sum of the axial dimensions of the first cylinder 200 and the second cylinder 300 is constant, the diameter of the air intake port 2011 can be increased by making the axial dimension of the first cylinder 200 larger than the axial dimension of the second cylinder 300, thereby increasing the air intake cross-sectional area. This solves the problem of insufficient air intake and increased flow rate caused by the small air intake cross-sectional area of ​​the compressor 600 in the related art.

[0104] Specifically, when the sum of the axial dimension H1 of the first cylinder 200 and the axial dimension H2 of the second cylinder 300 is constant, the larger the axial dimension H1 of the first cylinder 200, the smaller the axial dimension H2 of the second cylinder 300. The larger axial dimension H1 of the first cylinder 200 is conducive to increasing the diameter of the air intake port 2011, increasing the cross-sectional area of ​​the air intake port 2011, and thus increasing the high-frequency air intake volume of the compressor 600. When the air intake cross-sectional area increases, the air intake flow rate will decrease accordingly, the air intake pulsation will also decrease accordingly, and the vibration of the compressor 600 will be reduced.

[0105] For example, when the sum of the axial dimension H1 of the first cylinder 200 and the axial dimension H2 of the second cylinder 300 is constant, compared with the case in the related art where the axial dimension of the upper cylinder is equal to the axial dimension of the lower cylinder, if the positions of the split inlet are the same, the axial dimension of the first cylinder 200 is larger than the axial dimension of the second cylinder 300, so that the axial dimension H2 of the second cylinder 300 becomes smaller, the angle between the axis of the intake passage 201 and the axis of the split passage 400 increases, so that the fluid resistance is reduced, the power of the compressor 600 is reduced, and the energy efficiency of the compressor 600 is improved.

[0106] In this embodiment, when the air intake passage 201 is inclined toward the second cylinder 300 along the direction from the air intake port 2011 to the air outlet port 2012, the bending angle ɑ of the air intake elbow 602 is greater than 90° to allow the gas to enter the inclined air intake passage 201 more smoothly, reduce flow resistance, and improve the smoothness and continuity of gas flow.

[0107] Optionally, the compressor 600 includes a twin-cylinder rotor type compressor.

[0108] Combination Figures 1 to 5 As shown, optionally, the intake elbow 602 includes a first pipe and a second pipe connected to each other. The first pipe is connected to the outlet of the liquid reservoir 601. The second pipe is connected to the air intake port 2011 of the intake channel 201 of the cylinder assembly 100. The first pipe is arranged vertically. The angle ɑ between the first pipe and the second pipe is greater than 90°.

[0109] The above description and the accompanying drawings sufficiently illustrate the embodiments of the present disclosure to enable those skilled in the art to practice them. Other embodiments may include structural and other changes. The embodiments represent only possible variations. Unless explicitly required, individual components and functions are optional, and the order of operations may vary. Portions and features of some embodiments may be included in or replace portions and features of other embodiments. The embodiments of the present disclosure are not limited to the structures described above and shown in the accompanying drawings, and various modifications and changes may be made without departing from the scope thereof. The scope of the present disclosure is limited only by the appended claims.

Claims

1. A cylinder assembly, characterized in that: include: A first cylinder including an air intake passage having an air intake port and an air outlet port; A second cylinder is coaxially arranged with the first cylinder; A flow dividing channel is provided in the first cylinder and the second cylinder; one end of the flow dividing channel is a flow dividing inlet and is connected to the air inlet channel, and the other end of the flow dividing channel is a flow dividing outlet and is located on the inner wall of the second cylinder; Wherein, the axial dimension of the first cylinder is greater than the axial dimension of the second cylinder; The gas enters the intake channel through the air intake port and then is split, entering the first cylinder through the air outlet and entering the second cylinder through the split channel.

2. The cylinder assembly according to claim 1, characterized in that: Along the direction from the air intake port to the air outlet port, the air intake passage is inclined toward a direction close to the second cylinder.

3. The cylinder assembly according to claim 2, characterized in that: The first cylinder also includes: The flared portion is arranged at the air outlet end of the air intake passage and is located at a side away from the second cylinder; and the flared portion and the air outlet are connected to form an expanded air outlet.

4. The cylinder assembly according to claim 3, characterized in that: The distance from the upper edge point of the expanded air outlet to the upper end of the first cylinder is equal to the distance from the lower edge point of the expanded air outlet to the lower end of the first cylinder.

5. The cylinder assembly according to any one of claims 1 to 4, characterized in that: The axial dimension H1 of the first cylinder and the axial dimension H2 of the second cylinder satisfy: H2 <H1≤1.8H2。 6. The cylinder assembly according to any one of claims 1 to 4, characterized in that: The included angle β between the axis of the intake channel and the axis of the bypass channel satisfies: 90°≤β<165°。 7. The cylinder assembly according to any one of claims 1 to 4, characterized in that: Also includes: a partition plate disposed between the first cylinder and the second cylinder; The flow diversion channel penetrates through the partition.

8. The cylinder assembly according to claim 7, characterized in that: The diversion channels include: A first flow distribution channel is opened in the first cylinder; A second flow distribution channel is provided in the partition; A third flow distribution channel is opened in the second cylinder; Among them, the first diversion channel, the second diversion channel and the third diversion channel are connected in sequence, the end of the first diversion channel away from the second diversion channel is the diversion inlet, and the end of the third diversion channel away from the second diversion channel is the diversion outlet.

9. The cylinder assembly according to claim 8, characterized in that: The axis of the first diversion channel, the axis of the second diversion channel, and the axis of the third diversion channel are located in the same straight line or are not located in the same straight line; When the axes of the first diverter channel, the second diverter channel and the third diverter channel are not located in the same straight line, the angle between the axis of the first diverter channel and the axis of the intake channel is smaller than the angle between the axis of the second diverter channel and the axis of the intake channel, and the angle between the axis of the second diverter channel and the axis of the intake channel is smaller than the angle between the axis of the third diverter channel and the axis of the intake channel.

10. A compressor, characterized in that: include: The cylinder assembly according to any one of claims 1 to 9; Liquid reservoir; An intake elbow, one end of which is connected to the outlet of the liquid reservoir and the other end of which is connected to the air intake port of the intake passage of the cylinder assembly; When the air intake passage is inclined toward the second cylinder along the direction from the air intake port to the air outlet, the bending angle of the air intake elbow is greater than 90°.

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