Cylinder assembly and compressor

Abstract

The application relates to the technical field of compressors, and discloses a cylinder assembly and a compressor. The cylinder assembly comprises a first cylinder, a second cylinder and a shunt passage. The first cylinder comprises an air inlet channel with an air suction port and an air outlet port. The second cylinder is coaxially arranged with the first cylinder. The shunt passage is arranged on the first cylinder and the second cylinder. One end of the shunt passage is a shunt inlet and is in communication with the air inlet channel, and the other end of the shunt passage is a shunt outlet and is located on the inner wall of the second cylinder. The axial dimension of the first cylinder is greater than the axial dimension of the second cylinder. After air enters the air inlet channel through the air suction port, the air is shunted, enters the first cylinder through the air outlet port and enters the second cylinder through the shunt passage. In the application, the axial dimension of the first cylinder is greater than the axial dimension of the second cylinder, so that the diameter of the air suction port can be increased, the air inlet cross-sectional area can be increased, the air suction amount during high-frequency operation of the compressor can be increased, and the air suction efficiency can be improved.

Description

Technical Field

[0001] This application relates to the field of compressor technology, such as to a cylinder assembly and a compressor. Background Technology

[0002] Currently, the design of a twin-cylinder rotary compressor with its receiver connected to two intake pipes has become a trend to reduce the cost of the compressor.

[0003] In related technologies, a twin-cylinder rotary compressor includes a liquid receiver, an upper cylinder, and a lower cylinder. The height of the upper cylinder is equal to the height of the lower cylinder, meaning that the axial dimensions of the upper cylinder and the lower cylinder are equal. The liquid receiver is connected to the upper cylinder via an inlet pipe, and gas enters the upper cylinder from the inlet pipe and is then diverted to the lower cylinder.

[0004] In the process of implementing the embodiments of this disclosure, at least the following problems were found in the related art:

[0005] In the related technology of twin-cylinder rotary compressors, when the sum of the axial dimensions of the upper and lower cylinders is constant, the axial dimension of the upper cylinder limits the diameter of its intake port. This prevents the intake cross-sectional area from increasing, resulting in insufficient intake volume during high-frequency operation and an increase in intake gas velocity. The increased intake gas velocity leads to increased flow resistance and pulsation, ultimately reducing intake efficiency.

[0006] Furthermore, when the axial dimensions of the upper cylinder and the lower cylinder are equal, in order to ensure that the lower cylinder outlet delivers air evenly into the lower cylinder cavity, the stroke from the upper cylinder intake port to the lower cylinder outlet is relatively large. This limits the angle between the upper cylinder intake passage and the lower cylinder branch passage, resulting in higher flow resistance, increased compressor power, and decreased energy efficiency.

[0007] It should be noted that the information disclosed in the background section above is only used to enhance the understanding of the background of this application, and therefore may include information that does not constitute prior art known to those skilled in the art. Summary of the Invention

[0008] To provide a basic understanding of some aspects of the disclosed embodiments, a brief summary is given below. This summary is not intended as a general commentary, nor is it intended to identify key / important components or describe the scope of protection of these embodiments, but rather as a prelude to the detailed description that follows.

[0009] This disclosure provides a cylinder assembly and a compressor to increase the intake volume, improve intake efficiency, and reduce gas flow resistance during high-frequency operation of the compressor.

[0010] In some embodiments, a cylinder assembly is provided, comprising: a first cylinder, the first cylinder including an intake passage having an intake port and an outlet port; a second cylinder, coaxially disposed with the first cylinder; and a flow divider channel formed in the first cylinder and the second cylinder; one end of the flow divider channel is a flow divider inlet and connected to the intake passage, and the other end of the flow divider channel is a flow divider outlet and located on the inner wall of the second cylinder; wherein, the axial dimension of the first cylinder is larger than the axial dimension of the second cylinder; gas enters the intake passage through the intake port and is then divided, entering the first cylinder through the outlet port and entering the second cylinder through the flow divider channel.

[0011] Optionally, the intake passage is inclined toward the second cylinder along the direction from the intake port to the exhaust port.

[0012] Optionally, the first cylinder further includes: a flared portion, disposed at the outlet end of the intake passage and located on the side away from the second cylinder; and the flared portion communicates with the outlet to form an expanded outlet.

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

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

[0015] Optionally, on the axial section of the first cylinder at the upper edge point of the expanded air outlet, the angle between the upper edge line of the flared portion and the 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 the following:

[0018] H2

[0019] Optionally, the angle β between the axis of the intake passage and the axis of the splitter passage satisfies:

[0020] 90°≤β<165°.

[0021] Optionally, the cylinder assembly further includes: a partition disposed between the first cylinder and the second cylinder; and a flow divider extending through the partition.

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

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

[0024] Optionally, the axes of the first, second, and third flow dividers may be on the same straight line or not on the same straight line. If the axes of the first, second, and third flow dividers are not on the same straight line, the angle between the axis of the first flow divider and the axis of the intake channel is smaller than the angle between the axis of the second flow divider and the axis of the intake channel, and the angle between the axis of the second flow divider and the axis of the intake channel is smaller than the angle between the axis of the third flow divider and the axis of the intake channel.

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

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

[0027] 90°≤β1<β2<β3<165°.

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

[0029] Alternatively, the compressor may include a twin-cylinder rotary compressor.

[0030] Optionally, the intake bend includes a first pipe and a second pipe that are connected. The first pipe is connected to the outlet of the reservoir. The second pipe is connected to the intake port of the cylinder assembly's intake passage. The first pipe is vertically positioned. The angle between the first pipe and the second pipe is greater than 90°.

[0031] The cylinder assembly and compressor provided in this disclosure can achieve the following technical effects:

[0032] The cylinder assembly provided in this embodiment, with the sum of the axial dimensions of the first cylinder and the second cylinder being constant, can increase the diameter of the intake port and the intake cross-sectional area by making the axial dimension of the first cylinder larger than that of the second cylinder, thereby increasing the intake volume and improving the intake efficiency during high-frequency operation of the compressor.

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

[0034] The above general description and the description below are exemplary and illustrative only and are not intended to limit this application. Attached Figure Description

[0035] One or more embodiments are illustrated by way of example with reference to the accompanying drawings. These illustrations and drawings do not constitute a limitation on the embodiments. Elements having the same reference numerals in the drawings are shown as similar elements. The drawings are not to be scaled. And wherein:

[0036] Figure 1 This is a cross-sectional schematic diagram of a compressor provided in one embodiment of this 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 This is a cross-sectional schematic diagram of a compressor provided in another embodiment of this disclosure;

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

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

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

[0043] Figure label:

[0044] 100: Cylinder assembly;

[0045] 200: First cylinder; 201: Intake passage; 2011: Intake port; 2012: Exit port; 202: Flaring section;

[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 receiver; 602: Inlet bend. Detailed Implementation

[0050] To provide a more detailed understanding of the features and technical content of the embodiments of this disclosure, the implementation of the embodiments of this disclosure will be described in detail below with reference to the accompanying drawings. The accompanying drawings are for illustrative purposes only and are not intended to limit the embodiments of this disclosure. In the following technical description, for ease of explanation, several details are used to provide a full understanding of the disclosed embodiments. However, one or more embodiments may still be implemented without these details. In other cases, well-known structures and devices may be simplified in their depiction to simplify the drawings.

[0051] The terms "first," "second," etc., used in the specification, claims, and accompanying drawings of this disclosure are used to distinguish similar objects and are not necessarily used to describe a specific order or sequence. It should be understood that such data can be interchanged where appropriate for the embodiments of this disclosure described herein. Furthermore, the terms "comprising" and "having," and any variations thereof, are intended to cover non-exclusive inclusion.

[0052] In this disclosure, the terms "upper," "lower," "inner," "middle," "outer," "front," and "rear," etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. These terms are primarily for better description of the embodiments of this disclosure and their implementations, and are not intended to limit the indicated devices, elements, or components to having a specific orientation, or to require them to be constructed and operated in a specific orientation. Furthermore, some of the aforementioned terms may be used to indicate other meanings besides orientation or positional relationship; for example, the term "upper" may in some cases indicate a dependency or connection relationship. Those skilled in the art can understand the specific meaning of these terms in the embodiments of this disclosure according to the specific circumstances.

[0053] Furthermore, the terms "set up," "connect," and "fix" should be interpreted broadly. For example, "connection" 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, components, or parts. Those skilled in the art can understand the specific meaning of the above terms in the embodiments of this disclosure according to the specific circumstances.

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

[0055] It should be noted that, unless otherwise specified, the embodiments and features described in the present disclosure can be combined with each other.

[0056] Combination Figures 1 to 7 As shown, this 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 flow divider 400. The first cylinder 200 includes an intake passage 201 having an intake port 2011 and an outlet port 2012. The second cylinder 300 is coaxially arranged with the first cylinder 200. The flow divider 400 is formed in both the first cylinder 200 and the second cylinder 300. One end of the flow divider 400 is a flow divider inlet and communicates with the intake passage 201, and the other end is a flow divider outlet located on the inner wall of the second cylinder 300. The axial dimension of the first cylinder 200 is larger than that of the second cylinder 300. Gas enters the intake passage 201 through the intake port 2011 and is then divided, entering the first cylinder 200 through the outlet port 2012 and the second cylinder 300 through the flow divider 400.

[0057] The cylinder assembly 100 provided in this embodiment, when the sum of the cylinder height of the first cylinder 200 and the cylinder height of the second cylinder 300 is constant, that is, when the sum of the axial dimensions of the first cylinder 200 and the second cylinder 300 is constant, can increase the diameter of the intake port 2011 and increase the intake cross-sectional area by making the axial dimension of the first cylinder 200 greater than that of the second cylinder 300, thereby increasing the intake volume and improving the intake efficiency of the compressor 600 during high-frequency operation.

[0058] The cylinder assembly 100 provided in this embodiment of the present disclosure, by having the axial dimension of the first cylinder 200 greater than that of the second cylinder 300, achieves uniform air delivery from the diversion outlet to the second cylinder 300, while reducing the stroke from the intake port 2011 of the first cylinder 200 to the diversion outlet of the second cylinder 300, increasing the angle between the axis of the intake channel 201 and the axis of the diversion channel 400, reducing gas flow resistance, and improving the energy efficiency of the compressor 600.

[0059] Specifically, the diversion outlet is located in the middle of the inner wall of the second cylinder 300. The diversion outlet is not located at the upper or lower part of the inner wall of the second cylinder 300, so that the diversion outlet can uniformly deliver gas into the middle of the second cylinder 300, thereby achieving uniform gas delivery into the second cylinder 300.

[0060] Compared to related technologies where the height of the upper cylinder is equal to that of the lower cylinder, this embodiment, by uniformly supplying air to the second cylinder 300 through the diversion outlet, reduces the stroke from the intake port 2011 of the first cylinder 200 to the diversion outlet of the second cylinder 300 by making the axial dimension of the second cylinder 300 smaller than that of the first cylinder 200. This increases the angle between the axis of the intake channel 201 and the axis of the diversion channel 400, thereby reducing gas flow resistance.

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

[0062] In this embodiment, by tilting the intake channel 201, the gas drawn into the intake channel 201 is more easily diverted to the diversion channel 400, thereby making the gas drawn into the intake port 2011 of the first cylinder 200 more smoothly diverted to the second cylinder 300, reducing 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 outlet 2012 end of the intake passage 201 and is located on the side away from the second cylinder 300. The flared portion 202 communicates with the outlet 2012 to form an expanded outlet 2012.

[0064] In this embodiment, when the intake passage 201 is inclined toward the direction of the second cylinder 300, by providing a flared part 202 at the outlet 2012 end of the intake passage 201, the local eddy current loss 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 expansion outlet 2012 to the upper end of the first cylinder 200 is equal to the distance from the lower edge of the expansion 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 flared outlet 2012 to the upper end of the first cylinder 200 is equal to the distance from the lower edge of the flared outlet 2012 to the lower end of the first cylinder 200. This ensures that the gas drawn in by the intake port 2011 of the first cylinder 200 is uniformly delivered into the compression chamber of the first cylinder 200 through the flared outlet 2012.

[0067] Specifically, because the intake passage 201 is inclined towards the second cylinder 300, the gas drawn into the intake port 2011 enters the compression chamber of the first cylinder 200 through the intake passage 201 and is located in the lower part of the compression chamber. By providing the flared part 202, the distance from the upper edge of the flared outlet 2012 to the upper end of the first cylinder 200 is equal to the distance from the lower edge of the flared outlet 2012 to the lower end of the first cylinder 200, thereby ensuring that the gas delivered into the compression chamber of the first cylinder 200 is located in the middle of the compression chamber, thus improving the uniformity of gas delivery.

[0068] Furthermore, this embodiment increases the gas flow rate by providing the flared section 202, thereby reducing the gas flow rate, reducing airflow pulsation, and also reducing local eddy current losses.

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

[0070] In this embodiment, by using L≥1mm, the gas entering the compression chamber of the first cylinder 200 is made uniform, while the strength and operational reliability of the first cylinder 200 are improved.

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

[0072] Optionally, 30°≤θ≤60°.

[0073] In this embodiment, by using 30°≤θ≤60°, the distance from the upper edge of the expansion outlet 2012 to the upper end of the first cylinder 200 is equal to the distance from the lower edge of the expansion 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 the following:

[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] For example, in combination Figure 6 As shown, when the cylinder assembly 100 is applied to the compressor 600, taking the compressor 600's operating frequency of 90Hz as an example, the effect of the compressor 600's low-temperature heating capacity is verified. With the sum of the axial dimensions H1 of the first cylinder 200 and H2 of the second cylinder 300 constant, the low-temperature heating capacity (unit: W) of the compressor 600 is tested under four conditions: H1 = H2, H1 = 1.2H2, H1 = 1.5H2, and H1 = 1.8H2. The test results are as follows: 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; and when H1 = 1.8H2, the low-temperature heating capacity of the compressor 600 is 11038W. It can be seen that the low-temperature heating capacity of compressor 600 is greater in the cases where H1 = 1.2H2, H1 = 1.5H2, and H1 = 1.8H2 than in the case where H1 = H2. Therefore, when the sum of the axial dimensions H1 of the first cylinder 200 and H2 of the second cylinder 300 is constant, the low-temperature heating capacity of 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] For example, in combination Figure 7 ​​As shown, when the cylinder assembly 100 is applied to the compressor 600, taking the operating frequency of the compressor 600 as 120Hz as an example, the effect of the compressor 600 in low-temperature heating is verified. With the sum of the axial dimensions H1 of the first cylinder 200 and H2 of the second cylinder 300 constant, the low-temperature heating capacity (unit: W) of the compressor 600 is tested under four conditions: H1=H2, H1=1.2H2, H1=1.5H2, and H1=1.8H2. The test results are as follows: 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; and when H1=1.8H2, the low-temperature heating capacity of the compressor 600 is 14717W. It can be seen that the low-temperature heating capacity of compressor 600 is greater in the cases where H1 = 1.2H2, H1 = 1.5H2, and H1 = 1.8H2 than in the case where H1 = H2. Therefore, when the sum of the axial dimensions H1 of the first cylinder 200 and H2 of the second cylinder 300 is constant, the low-temperature heating capacity of 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 intake passage 201 and the axis of the split passage 400 satisfies:

[0080] 90°≤β<165°.

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

[0082] For example, in combination Figure 3As shown, the angle β between the axis of the intake passage 201 and the axis of the split passage 400 is related to the horizontal distance A from the center of the split inlet to the inner wall of the first cylinder 200 and the vertical distance B from the center of the split inlet to the center of the split outlet. In practical applications, the value of the horizontal distance A from the center of the split inlet to the interior of the first cylinder 200 is fixed. The smaller the vertical distance B from the center of the split inlet to the center of the split outlet, the larger the angle β between the axis of the intake passage 201 and the axis of the split passage 400. The vertical distance B from the center of the split inlet to the center of the split outlet is related to the distance L from the lower edge of the expansion outlet 2012 to the lower end of the first cylinder 200, the axial dimension T of the baffle 500, and the distance from the center of the split outlet to the upper end of the second cylinder 300. In practical applications, the distance L from the lower edge of the expansion outlet 2012 to the lower end of the first cylinder 200 and the axial dimension T of the baffle 500 are both taken as 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 diversion outlet to the upper end of the second cylinder 300 can be reduced, thereby reducing the vertical distance B from the center of the diversion inlet to the center of the diversion outlet, increasing the angle β between the axis of the intake channel 201 and the axis of the diversion channel 400, thereby reducing 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 500. The partition 500 is disposed between the first cylinder 200 and the second cylinder 300. A flow diversion channel 400 extends through the partition 500.

[0084] In this embodiment, by setting a partition 500 and a diversion channel 400 through the partition 500, the cylinder assembly 100 is made to operate stably.

[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 diversion channel 400 includes a first diversion channel 401, a second diversion channel 402, and a third diversion channel 403. The first diversion channel 401 is located in the first cylinder 200. The second diversion channel 402 is located in the partition 500. The third diversion channel 403 is located in the second cylinder 300. The first diversion channel 401, the second diversion channel 402, and the third diversion channel 403 are sequentially connected. The end of the first diversion channel 401 furthest from the second diversion channel 402 is the diversion inlet. The end of the third diversion channel 403 furthest from the second diversion channel 402 is the diversion outlet.

[0088] In this embodiment, by opening a first diversion channel 401 in the first cylinder 200, a second diversion channel 402 in the partition 500, and a third diversion channel 403 in the second cylinder 300, and by connecting the first diversion channel 401, the second diversion channel 402, and the third diversion channel 403 in sequence, the gas drawn into the intake channel 201 enters the second cylinder 300 through the diversion channel 400, thus enabling the second cylinder 300 to work smoothly.

[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 on the same straight line.

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

[0091] Optionally, the angle β between the straight line passing through 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 and the axis of the intake 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: °), diameter (unit: mm), and cross-sectional area (unit: mm) of the intake port 2011 and the splitter channel 400 are as follows: H1 = H2, H1 = 1.2H2, H1 = 1.5H2, and H1 = 1.8H2. 2 ) and intake port cross-sectional area 2011 / compressor displacement 600 (mm) 2 / cm 3 As shown in Table 1. According to Table 1, the ratio of the intake port 2011 cross-sectional area to the compressor 600 displacement is greater in the cases where H1 = 1.2H2, H1 = 1.5H2, and H1 = 1.8H2 than in the case where H1 = H2. Therefore, when the sum of the axial dimensions H1 of the first cylinder 200 and H2 of the second cylinder 300 remains constant, the 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 axes of the first diversion channel 401, the second diversion channel 402, and the third diversion channel 403 are not collinear. When the axes of the first diversion channel 401, the second diversion channel 402, and the third diversion channel 403 are not collinear, the angle between the axis of the first diversion channel 401 and the axis of the intake channel 201 is smaller than the angle between the axis of the second diversion channel 402 and the axis of the intake channel 201. Furthermore, the angle between the axis of the second diversion channel 402 and the axis of the intake channel 201 is smaller than the angle between the axis of the third diversion channel 403 and the axis of the intake channel 201.

[0096] In this embodiment, the axes of the first diversion channel 401, the second diversion channel 402, and the third diversion channel 403 are not on the same straight line, and the angles between the axes of the first diversion channel 401, the second diversion channel 402, and the third diversion channel 403 and the axis of the intake channel 201 gradually increase. This allows the gas drawn into the intake channel 201 to enter the second cylinder 300 more smoothly, thereby making the gas path into the compression chamber of the second cylinder 300 smoother and improving the working performance of the cylinder assembly 100.

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

[0098] 90°≤β1<β2<β3<165°.

[0099] It is understood that the ends of the first diversion channel 401 and the second diversion channel 402 connected to each other are of equal size and have the same structure, and the ends of the second diversion channel 402 and the third diversion channel 403 connected to each other are of equal size and have the same 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 shape of the first diversion channel 401, the second diversion channel 402, and the third diversion channel 403 is not limited and can be set as needed. For example, the radial cross-section of the first diversion channel 401, the second diversion channel 402, and the third diversion channel 403 can be circular, elliptical, etc.

[0101] Combination Figures 1 to 7As shown, this embodiment of the present disclosure also provides a compressor 600. The compressor 600 includes a cylinder assembly 100, a liquid reservoir 601, and an intake bend 602 as described above. One end of the intake bend 602 is connected to the outlet of the liquid reservoir 601, and the other end of the intake bend 602 is connected to the intake port 2011 of the intake passage 201 of the cylinder assembly 100. When the intake passage 201 is inclined towards the second cylinder 300 along the direction from the intake port 2011 to the outlet 2012, the bending angle α of the intake bend 602 is greater than 90°.

[0102] In this embodiment, the other end of the intake bend 602 can extend into the intake passage 201 of the first cylinder 200. After the gas enters the intake passage 201, it is split, entering the first cylinder 200 through the outlet 2012, and entering the second cylinder 300 through the splitting passage 400. The axial dimension of the first cylinder 200, which is connected to the intake bend 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. This is beneficial to increasing the diameter of the suction port 2011 to meet the suction volume requirements of the compressor 600.

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

[0104] Specifically, when the sum of the axial dimensions H1 of the first cylinder 200 and H2 of the second cylinder 300 remains constant, the larger the axial dimension H1 of the first cylinder 200, the smaller the axial dimension H2 of the second cylinder 300. A larger axial dimension H1 of the first cylinder 200 is beneficial for increasing the diameter of the intake port 2011, increasing the cross-sectional area of ​​the intake port 2011, and thus increasing the high-frequency intake volume of the compressor 600. When the intake cross-sectional area increases, the intake air velocity will decrease accordingly, the intake pulsation will also decrease accordingly, and the vibration of the compressor 600 will decrease accordingly.

[0105] For example, when the sum of the axial dimensions H1 of the first cylinder 200 and H2 of the second cylinder 300 is constant, compared to the case in the related art where the axial dimensions of the upper cylinder and the lower cylinder are equal, if the positions of the flow divider inlets are the same, by making the axial dimension of the first cylinder 200 larger than that of the second cylinder 300, thus making the axial dimension H2 of the second cylinder 300 smaller, the angle between the axis of the intake passage 201 and the axis of the flow divider passage 400 will increase, thereby reducing fluid resistance, reducing the power of the compressor 600, and improving the energy efficiency of the compressor 600.

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

[0107] Optionally, compressor 600 includes a twin-cylinder rotary compressor.

[0108] Combination Figures 1 to 5 As shown, optionally, the intake bend 602 includes a first pipe and a second pipe that are connected. The first pipe is connected to the outlet of the reservoir 601. The second pipe is connected to the intake port 2011 of the intake passage 201 of the cylinder assembly 100. The first pipe is vertically arranged. The included angle α between the first pipe and the second pipe is greater than 90°.

[0109] The foregoing description and accompanying drawings fully illustrate 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. Individual components and functions are optional unless explicitly required, and the order of operation may vary. Parts and features of some embodiments may be included or substituted for parts and features of other embodiments. 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 its scope. The scope of the present disclosure is limited only by the appended claims.

Claims

1. A cylinder assembly, characterized in that, include: The first cylinder includes an intake passage with an intake port and an exhaust port; The second cylinder is coaxially arranged with the first cylinder; The flow divider is located in the first cylinder and the second cylinder; one end of the flow divider is the flow divider inlet and is connected to the intake passage, and the other end of the flow divider is the flow divider outlet and is located on the inner wall of the second cylinder. A partition is disposed between the first cylinder and the second cylinder, and a flow diversion channel passes through the partition; The axial dimension of the first cylinder is greater than that of the second cylinder. Along the direction from the intake port to the exhaust port, the intake passage is inclined towards the direction of the second cylinder; The first cylinder also includes a flared section, which is located at the outlet end of the intake channel and on the side away from the second cylinder. The flared section and the outlet are connected to form an expanded outlet. The distance from the upper edge of the expanded outlet to the upper end of the first cylinder is equal to the distance from the lower edge of the expanded outlet to the lower end of the first cylinder. The distance from the lower edge of the expanded outlet to the lower end of the first cylinder and the axial dimension of the partition are both taken as the minimum value within the allowable range. After the gas enters the intake channel through the intake port, it is split and enters the compression chamber of the first cylinder through the outlet, where it is located in the middle of the compression chamber. Then, it enters the second cylinder through the split channel. With a fixed horizontal distance from the center of the split inlet to the interior of the first cylinder, the smaller the vertical distance from the center of the split inlet to the center of the split outlet, the larger the angle between the axis of the intake passage and the axis of the split passage.

2. The cylinder assembly according to claim 1, characterized in that, Axial dimension of the first cylinder Axial dimension of the second cylinder satisfy: 。 3. The cylinder assembly according to claim 1, characterized in that, The angle between the axis of the intake passage and the axis of the splitter passage satisfy: 。 4. The cylinder assembly according to claim 3, characterized in that, The diversion channels include: The first flow channel is located in the first cylinder; The second diversion channel is located within the partition; The third flow channel is located in the second cylinder; 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.

5. The cylinder assembly according to claim 1, characterized in that, The axes of the first diversion channel, the second diversion channel, and the third diversion channel may be on the same straight line or not on the same straight line; When the axes of the first, second, and third flow dividers are not on the same straight line, the angle between the axis of the first flow divider and the axis of the intake channel is smaller than the angle between the axis of the second flow divider and the axis of the intake channel, and the angle between the axis of the second flow divider and the axis of the intake channel is smaller than the angle between the axis of the third flow divider and the axis of the intake channel.

6. A compressor, characterized in that, include: Cylinder assembly as claimed in any one of claims 1 to 5; Liquid reservoir; The intake bend has one end connected to the outlet of the liquid reservoir and the other end connected to the intake port of the cylinder assembly's intake channel. When the intake passage is tilted towards the second cylinder along the direction from the intake port to the exhaust port, the bend angle of the intake bend is greater than 90°.

Images