WO2024032534A1

WO2024032534A1 - Compression mechanism and scroll compressor

Info

Publication number: WO2024032534A1
Application number: PCT/CN2023/111415
Authority: WO
Inventors: 刘轩; 刘鑫娴; 邹宏伟
Original assignee: 谷轮环境科技（苏州）有限公司
Priority date: 2022-08-08
Filing date: 2023-08-07
Publication date: 2024-02-15

Abstract

A compression mechanism, comprising: a fixed scroll, the fixed scroll comprising a fixed scroll end plate and a fixed scroll blade; a movable scroll, the movable scroll comprising a movable scroll end plate and a movable scroll blade, and the fixed scroll blade and the movable scroll blade being mutually engaged to form a series of compression cavities; and a back pressure cavity, the back pressure cavity being in fluid communication with a compression cavity by means of a back pressure channel so as to apply back pressure, the back pressure channel comprising an expanded section and narrowed sections formed on two opposite sides of the expanded section, and the fluid flow cross-sectional area of the expanded section being larger than that of each narrowed section. A scroll compressor comprising the compression mechanism has high reliability.

Description

Compression mechanism and scroll compressor

This application claims priority from the following Chinese patent applications: a Chinese patent application with application number 202210944867.7 and an invention title "Compression Mechanism and Scroll Compressor" submitted to the China Patent Office on August 8, 2022; The Chinese patent application with the application number 202222076401.8 and the invention name "Compression Mechanism and Scroll Compressor" was submitted to the China Patent Office on March 8. The entire contents of these patent applications are incorporated by reference into this application.

Technical field

The present disclosure relates to a compression mechanism and a scroll compressor having the compression mechanism.

Background technique

The contents in this section only provide background information related to the present disclosure and may not constitute prior art.

Scroll compressors can be used in refrigeration systems, air conditioning systems and heat pump systems, for example. As its main component, the compression mechanism of the scroll compressor is used to compress the working fluid (such as refrigerant). The compression mechanism includes a fixed scroll and an orbiting scroll that rotates in translation relative to the fixed scroll. Both the fixed scroll and the orbiting scroll include an end plate and spiral blades extending from one side of the end plate. When the orbiting scroll orbits relative to the fixed scroll, a series of moving compression cavities are formed between the fixed scroll and the spiral blades of the orbiting scroll, with the volume gradually decreasing from the radial outer side to the radial inner side, thus compressing the working fluid. .

A back pressure chamber is provided in the scroll compressor to provide back pressure for engaging the fixed scroll and the orbiting scroll in the axial direction. However, in the actual operation of the scroll compressor, there is a risk that the pressure in the back pressure chamber will fluctuate, resulting in a reduction in the working reliability of the compressor, and there is a risk that the working fluid will flow back into the compression chamber and cause repeated compression, resulting in energy loss of the scroll compressor. Risks of losses and wasted efficiency.

Therefore, there is a need to provide an improved compression mechanism and scroll compressor.

Contents of the invention

An object of one or more embodiments of the present disclosure is to provide a compression mechanism and a scroll compressor that have improved reliability and prevent energy loss and efficiency waste.

According to one aspect of the present disclosure, there is provided a compression mechanism including: a fixed scroll, which is an integral component and includes an integrally formed fixed scroll end plate and a fixed scroll blade, the fixed scroll blade is formed on the fixed scroll The first side of the movable scroll end plate; the movable scroll, the movable scroll includes the movable scroll end plate and the movable scroll blades formed on the first side of the movable scroll end plate, and the fixed scroll blades and the movable scroll blades interact with each other. joined to form a series of compression chambers capable of compressing the fluid therebetween; and a back pressure chamber in fluid communication with one of the series of compression chambers through a back pressure passage to exert an orbiting scroll and a fixed scroll Joint back pressure; characterized in that the back pressure passage includes an expansion section and a narrowing section formed on opposite sides of the expansion section, and the fluid flow cross-sectional area of the expansion section is greater than the fluid flow of each of the narrowing sections. Flow cross-sectional area.

Optionally, the central axis of one of the narrowing sections is offset from the central axis of the other of the narrowing sections.

Optionally, the back pressure channel includes two or more expansion sections, and each of the expansion sections is formed with constriction sections on opposite sides.

Optionally, the back pressure passage is formed in the fixed scroll end plate and extends through the fixed scroll end plate. The fixed scroll further includes a fixed scroll hub formed between the fixed scroll end plate and the fixed scroll end plate. On the second side opposite to the first side, the fixed scroll hub includes a first annular hub and a second annular hub, and the back pressure chamber is surrounded by the fixed scroll end plate, the first annular hub and the second annular hub. Space composition.

Optionally, the back pressure passage includes a first narrowing section open to a compression chamber and a second narrowing section open to the back pressure chamber, and the opposite sides of the fixed scroll end plate are processed with connected first drills. hole and a second drilled hole, the second drilled hole having a hole diameter larger than the first drilled hole and having an end open to the back pressure chamber, the end being mounted with a divider, the divider including a part that allows fluid flow therethrough The through hole and the blocking part that blocks the flow of fluid, the first narrowing section is formed by the first drilled hole, the second narrowed section is formed by the through hole, and the expansion section is formed by the part of the second drilled hole where the partition is not installed. form.

Optionally, the divider is removably mounted to the end of the second bore, and the divider includes a plurality of spaced through holes.

Optionally, a back pressure passage is formed in and extends through the orbiting scroll end plate, and the back pressure cavity is formed on a second side of the orbiting scroll end plate opposite to the first side.

Optionally, the axial length of the expansion section is greater than the axial length of each of the narrowing sections.

Optionally, each of the narrowing sections has the same flow cross-sectional area, and the fluid flow cross-sectional area of the expansion section is in the range of 1.1 to 1.5 times the flow cross-sectional area of the narrowing section, or, The narrowing sections have different fluid flow cross-sectional areas respectively, and the fluid flow cross-sectional area of the expansion section is in the range of 1.1 to 1.5 times the maximum fluid flow cross-sectional area of the narrowing section.

Other areas of application of the present disclosure will become apparent from the detailed description below. It should be understood that the detailed description and specific examples, while indicating preferred embodiments of the disclosure, are intended for purposes of illustration and are not intended to limit the disclosure.

Description of drawings

The features and advantages of one or more embodiments of the present disclosure will become more apparent from the following description with reference to the accompanying drawings, in which:

1 is a cross-sectional view showing a scroll compressor according to a comparative example;

Figures 2a and 2b are schematic diagrams showing changes in the compression chamber connected to the back pressure channel during the operation of the scroll compressor;

3 is a cross-sectional view showing a fixed scroll of the scroll compressor according to the first embodiment of the present disclosure;

4 is a cross-sectional view showing a fixed scroll of the scroll compressor according to the second embodiment of the present disclosure; and

5 is a cross-sectional view showing a fixed scroll of a scroll compressor according to a third embodiment of the present disclosure.

Detailed ways

Example embodiments will now be described more fully with reference to the accompanying drawings.

Example embodiments are provided so that this disclosure will be thorough, and will fully convey the scope to those skilled in the art. Numerous specific details are set forth, such as examples of specific components, devices, and methods, in order to provide a thorough understanding of the various embodiments of the disclosure. It will be apparent to those skilled in the art that specific details need not be employed, that example embodiments may be embodied in many different forms and should not be construed to limit the scope of the disclosure. In some exemplary embodiments, well-known processes, well-known device structures, and well-known technologies are not described in detail.

The overall structure of the scroll compressor 1 will be described below with reference to FIG. 1 . As shown in the figure, the scroll compressor 1 includes a compression mechanism, a motor, a rotating shaft, a main bearing seat 50 and an interior defining accommodating the scroll compression mechanism. Space shell.

The compression mechanism includes a fixed scroll 20 and an orbiting scroll 30 . The motor is configured to rotate the rotating shaft, and then the rotating shaft drives the movable scroll 30 to orbit relative to the fixed scroll 20 (that is, the central axis of the movable scroll moves around the central axis of the fixed scroll, but the movable scroll does not Rotate around its central axis) to compress the working fluid.

The fixed scroll 20 may be fixed relative to the housing body 10 in any suitable manner. The fixed scroll 20 may include a fixed scroll end plate 22 , a fixed scroll blade 24 formed on one side of the fixed scroll end plate 22 , and a fixed scroll hub formed on the other side of the fixed scroll end plate 22 . The non-orbiting scroll hub may include a first annular hub 26 and a second annular hub 28 .

The orbiting scroll 30 may include an orbiting scroll end plate 32 and an orbiting scroll blade 34 formed on one side of the orbiting scroll end plate 32 . The fixed scroll blades 24 and the orbiting scroll blades 34 are capable of engaging each other such that a series of volumes are formed between the fixed scroll blades 24 and the orbiting scroll blades 34 from radially outward to radially inward when the scroll compressor is operating. The gradually decreasing moving compression chamber achieves compression of the working fluid.

The main bearing seat 50 is adapted to support the orbiting scroll end plate 32 of the orbiting scroll 30 . The orbiting scroll end plate 32 orbits on the supporting surface of the main bearing seat 50 . The main bearing housing 50 may be fixed relative to the casing body 10 of the scroll compressor 1 by any suitable means.

In normal operation of the compressor 1, the fixed scroll 20 and the orbiting scroll 30 must engage each other in the axial direction to compress the working fluid. In addition, in order to provide a certain axial flexibility to the scroll assembly to increase the reliability and safety of the compressor, a back pressure chamber is usually provided for one of the fixed scroll 20 and the movable scroll 30 , so that the fixed scroll 20 The orbiting scroll 30 can reliably engage with each other under the action of back pressure. As shown in FIG. 1 , a first annular hub 26 is formed around the exhaust port 40 . The back pressure chamber 70 is formed by the space surrounded by the fixed scroll end plate 22, the first annular hub 26 and the second annular hub 28 and is closed by a seal assembly disposed therein. The back pressure chamber 70 is in fluid communication with one of a series of compression chambers between the orbiting scroll 30 and the fixed scroll 20 through the back pressure channel 60 formed in the fixed scroll end plate 22 , thereby exerting force on the orbiting scroll 30 The back pressure in the back pressure chamber 70 can effectively press the fixed scroll 20 and the orbiting scroll 30 together.

However, during the operation of the scroll compressor, the volume of the compression chamber connected to the back pressure passage 60 and the corresponding pressure change dynamically. Specifically, as shown in Figure 2(a), the back pressure channel is connected to a smaller compression chamber (shaded area), and the pressure in the compression chamber is larger. At this time, the fluid in the compression chamber flows into the back pressure chamber. middle; as the movable scroll 30 revolves around the fixed scroll 20, as shown in Figure 2(b), the back pressure channel will be connected to the larger compression chamber (the shaded area), and the pressure in the compression chamber will Small, at this time, the fluid in the back pressure chamber flows back into the compression chamber. The fluid injected back into the compression chamber will be vortexed The scroll compressor repeatedly compresses, which will lead to energy loss and efficiency waste of the scroll compressor. Moreover, because the pressure in the back pressure chamber fluctuates with the compression process and cannot remain stable, the reliability of the scroll compressor is reduced.

In order to solve the above problems, the inventor of the present invention has conceived an improved compression mechanism and scroll compressor. This compression mechanism can not only reduce or prevent the back pressure fluctuation of the scroll compressor, but also prevent the backflow of fluid from the back pressure chamber. Repeated compression occurs in the compression chamber.

The scroll compressor according to the present disclosure will be described in further detail below with reference to FIGS. 3 to 5 , wherein the same reference numerals in the drawings represent the same components and detailed descriptions of these components will be omitted.

The scroll compressor according to the first embodiment of the present disclosure is similar in structure to the scroll compressor according to the comparative example described above, in which only the fixed scroll 20A shown in FIG. 3 is used instead of the scroll compressor according to the comparative example. Fixed scroll 20, other structures of the scroll compressor remain basically unchanged.

As shown in FIG. 3 , the fixed scroll 20A may be an integral component and include an integrally formed fixed scroll end plate 22 and a fixed scroll blade 24 , wherein the fixed scroll blade 24 may be formed on the fixed scroll end plate 22 the first side. The integrated fixed scroll refers to the fixed scroll formed as a single piece processed in one piece, rather than the split fixed scroll formed by connecting multiple parts. The non-orbiting scroll also includes a non-orbiting scroll hub 26, 28, which may be formed on a second side of the non-orbiting scroll end plate 22 opposite the first side. Obviously, the non-orbiting scroll hub portions 26, 28 are formed integrally with the non-orbiting scroll end plate 22, rather than being formed as two separate components that are mechanically connected or fixed to each other.

The fixed scroll end plate 22 may be provided with a back pressure passage 60A that fluidly communicates one compression chamber in a series of compression chambers with the back pressure chamber 70 . The back pressure passage 60A may include an expansion section 62A and constriction sections formed on opposite sides of the expansion section (herein, the constriction section opening to the compression chamber will be referred to as the first constriction section 64A, and The narrowed section opening to the back pressure chamber 70 is called the second narrowed section 66A). The fluid flow cross-sectional area of the expanded section 62A may be larger than the fluid flow cross-sectional area of either of the first narrowing section 64A and the second narrowing section 66A. In this article, the cross-section perpendicular to the direction of fluid movement is called the fluid flow cross-section, and its area is called the fluid flow cross-section area.

When the fluid flows from the compression chamber to the back pressure chamber, the fluid first flows through the first narrowing section 64A, and the fluid undergoes a process of becoming thinner and narrower from the larger fluid flow cross-sectional area in the compression chamber, so that the flow velocity becomes larger and the dynamic movement becomes smaller. The pressure increases and the static pressure decreases. Then the fluid enters the expansion section 62A from the first narrowing section 64A. The high-speed fluid sprayed from the first narrowing section 64A forms a high-speed main fluid in the middle of the expansion section 62A, and symmetrical vortices are formed on both sides of the main fluid. The high-speed main fluid continuously interacts with the vortices on both sides. The fluid is pulled forward by the high-speed main fluid in the middle, so that the speed of the high-speed main fluid in the middle decreases and the speed of the vortex fluid increases until the main flow in the middle is not enough to overcome the pressure difference, the vortex fluid flows back, and the middle fluid area is enlarged. At this time, the fluid passes through the second narrowing section 66A, the fluid flow cross-sectional area is reduced again, and the kinetic energy is rapidly transformed into pressure potential energy. As a result, the fluid experiences a double throttling effect. Similarly, when fluid flows from the back pressure chamber to the compression chamber, the fluid first flows through the second constriction section 66A, then enters the expansion section 62A from the second constriction section 66A, and finally flows through the first constriction In section 64A, the fluid also undergoes double throttling. As a result, the back pressure channel 60A can produce a secondary throttling effect. This enhanced throttling effect increases the flow resistance of the back pressure chamber and the compression chamber, allowing the back pressure in the back pressure chamber to remain stable and prevent the fluid from flowing. The flow back into the compression chamber causes repeated compression, thereby improving scroll compressor performance.

Preferably, the axial length of the expansion section 62A may be greater than the axial length of each of the first constriction section 64A and the second constriction section 66A, which may be further enhanced by increasing the axial length of the expansion section 62A. The throttling effect of the back pressure channel will further keep the back pressure stable and prevent repeated compression of the fluid. And preferably, the fluid flow cross-sectional area of the expansion section 62A may be in the range of 1.1 to 1.5 times the fluid flow cross-sectional area of the first narrowing section 66A or the second narrowing section 66A. It should be noted here that the first narrowing section 64A and the second narrowing section 66A may have the same fluid flow cross-sectional area. At this time, the fluid flow cross-sectional area of the expansion section 62A may be in the first narrowing section. The fluid flow cross-sectional area of the section 64A or the second narrow section 66A is within a range of 1.1 to 1.5 times. The first narrowing section 64A may also have a different fluid flow cross-sectional area than the second narrowing section 66A. In this case, the fluid flow cross-sectional area of the expansion section 62A may be between the first narrowing section 64A and the second narrowing section 64A. In the range of 1.1 to 1.5 times the larger fluid flow cross-sectional area in the narrow section 66A. By making the fluid flow cross-sectional area of the expansion section 62A only slightly larger than the fluid flow cross-sections of the first narrowing section 64A and the second narrowing section 66A, the throttling effect of the back pressure channel can be further enhanced, thereby maintaining The back pressure stabilizes and prevents repeated compression of the fluid.

For example, the opposite sides of the fixed scroll end plate 22 may be processed with connected first boreholes and second boreholes. The diameter of the second borehole is larger than the diameter of the first borehole and the second borehole has a diameter of Open to the end of the back pressure chamber 70, a partition 80A is installed in this end. The partition 80A may include a through hole 82A that allows fluid flow therethrough and a barrier 84A that blocks the flow of fluid. At this time, the first narrowing section 64A may be formed by the first drilled hole, the second narrowed section 66A may be formed by the through hole 82A, and the expansion section 62A may be formed by a portion of the second drilled hole where the partition 80 is not installed. form. The spacer may, for example, be a screw formed with an external thread for detachable mounting into the second bore. In this way, a fixed scroll with a secondary throttling effect can be easily machined. It is schematically shown in FIG. 3 that the partition 80A includes a plurality of spaced apart A through hole, of course, the separator can also be formed with other forms of through holes. It should be understood that in the case where the partition 80A includes a plurality of through holes, the fluid flow cross-sectional area of the second narrowing section 66A is the sum of the fluid flow cross-sectional areas of the plurality of through holes.

4 is a cross-sectional view showing a fixed scroll of the scroll compressor according to the second embodiment of the present disclosure. The fixed scroll 20B of the scroll compressor according to the second embodiment of the present disclosure is similar in structure to the fixed scroll 20A of the scroll compressor according to the first embodiment of the present disclosure described above, and the only difference is that The structure of the back pressure channel is different, and only the differences will be described in detail below.

The fixed scroll back pressure passage 60B according to the second embodiment of the present disclosure may include an expansion section 62B and first and second constriction sections 64B and 66B disposed on opposite sides of the expansion section, wherein , the fluid flow cross-sectional area of the expansion section 62B may be larger than the fluid flow cross-sectional area of each of the first narrowing section 64B and the second narrowing section 66B. Moreover, the central axis of the first narrowing section 64B and the central axis of the second narrowing section 66B are staggered. In the fixed scroll according to the second embodiment of the present disclosure, since the central axis of the first narrowing section 64B is offset from the central axis of the second narrowing section 66B, the fluid in the back pressure passage 60B will Generating more flow around the fluid causes greater flow resistance, thereby further improving the stability of the pressure in the back pressure chamber and further reducing the risk of fluid backflow into the compression chamber causing repeated compression, thus improving scroll compressor performance. . Figure 4 also shows an alternative embodiment of a divider 80B that may include a through hole 82B that allows fluid flow therethrough and a barrier 84B that blocks fluid flow. The through hole 82B may be a single through hole formed in the center of the partition 80B.

5 is a cross-sectional view showing a fixed scroll of the scroll compressor according to the third embodiment of the present disclosure. The fixed scroll 20C of the scroll compressor according to the third embodiment of the present disclosure is similar in structure to the fixed scroll 20A of the scroll compressor according to the first embodiment of the present disclosure described above, and the only difference is that The structure of the back pressure channel is different, and only the differences will be described in detail below.

The fixed scroll bias passage 60C according to the third embodiment of the present disclosure may include a plurality of expansion sections and narrowing sections disposed on opposite sides of each expansion section, wherein a fluid flow cross-section of the expansion section The area may be greater than the fluid flow cross-sectional area of each of the narrowed sections. The fluid undergoes multiple throttling in the back pressure channel 60C, causing the fluid to encounter greater flow resistance, thereby further improving the stability of the pressure in the back pressure chamber and further reducing the risk of fluid backflow into the compression chamber causing repeated compression. Improve scroll compressor performance.

In the above-described embodiment, by utilizing the back-pressure channel provided in the fixed scroll to improve the stability of the back-pressure chamber pressure and reduce the risk of repeated compression of the fluid due to fluid backflow into the compression chamber, This improves the performance of the scroll compressor. However, those skilled in the art can imagine that a back-pressure channel with a secondary throttling effect can also be provided in the movable scroll end plate to achieve the same purpose, that is, the back-pressure channel can extend through the movable scroll. The end plate communicates with the back pressure chamber formed on one side of the orbiting scroll. Specifically, a back pressure chamber may be formed in a space within the main bearing housing 50 and be in fluid communication with one of the series of compression chambers via a back pressure passage formed in the orbiting scroll end plate. In addition, although the exemplary embodiments of the present application show that the narrowing section has a uniform cross-sectional shape, those skilled in the art will understand that the narrowing section can also have any other suitable shape, such as a tapered shape. V-shaped shape, etc.

While the present disclosure has been described with reference to exemplary embodiments, it is to be understood that the present disclosure is not limited to the specific embodiments described and illustrated in detail herein, without departing from the scope defined by the claims. Various changes may be made to the exemplary embodiments by skilled artisans. It should also be understood that, provided that the technical solutions are not inconsistent, features of various embodiments may be combined with each other or may be omitted.

Claims

A compression mechanism including:

Fixed scroll (20A, 20B, 20C), the fixed scroll is an integral component and includes an integrally formed fixed scroll end plate (22) and a fixed scroll blade (24), which is formed on The first side of the fixed scroll end plate;

An orbiting scroll (30), which includes an orbiting scroll end plate (32) and an orbiting scroll blade (34) formed on a first side of the orbiting scroll end plate (32), And the fixed scroll blade (24) and the orbiting scroll blade (34) are engaged with each other to form a series of compression chambers capable of compressing fluid; and

A back pressure chamber (70) is in fluid communication with one of the series of compression chambers through a back pressure passage (60A, 60B, 60C) to exert the movable scroll (30) ) The back pressure that engages the fixed scroll (20A, 20B, 20C);

It is characterized in that the back pressure channel (60A, 60B, 60C) includes an expansion section (62A, 62B) and a narrowing section (64A, 66A) formed on opposite sides of the expansion section (62A, 62B). ; 64B, 66B), the fluid flow cross-sectional area of the expansion section is greater than the fluid flow cross-sectional area of each of the narrowing sections.
The compression mechanism of claim 1, wherein a central axis of one of the narrowed sections (64B, 66B) is aligned with the other of the narrowed sections (64B, 66B). The central axes of the narrow sections are staggered.
The compression mechanism of claim 1, wherein the back pressure passage (60C) includes two or more expansion sections, and opposite sides of each of the expansion sections are formed There is a narrowing section.
The compression mechanism according to any one of claims 1-3, wherein the back pressure passage (60A, 60B, 60C) is formed in the fixed scroll end plate (22) and extends through the a fixed scroll end plate, the fixed scroll further comprising a fixed scroll hub formed on a second side of the fixed scroll end plate opposite to the first side, the The fixed scroll hub includes a first annular hub (26) and a second annular hub (28). The back pressure chamber (70) is composed of the fixed scroll end plate (22), the first annular hub (26) and the space surrounded by the second annular hub (28).
The compression mechanism of claim 4, wherein the back pressure passage (60A, 60B, 60C) includes a first constriction section (64A, 64B) opening to the one compression chamber and a first constriction section (64A, 64B) opening to the back pressure passage. In the second narrowed section (66A, 66B) of the pressure chamber, connected first boreholes and second boreholes are processed on opposite sides of the fixed scroll end plate, and the aperture of the second borehole is larger than that of the fixed scroll end plate. The first borehole has an aperture and the second borehole has an end open to the back pressure chamber, the end is mounted with a divider (80A, 80B), the divider includes a structure that allows fluid flow therethrough through holes (82A, 82B) and blocking portions (84A, 84B) that block fluid flow, the first narrowing section (64A, 64B) is formed by the first drilled hole, and the second narrowing portion Segments (66A, 66B) are formed by said through-holes and said expansion sections (62A, 62B) are formed by portions of said second boreholes where said partitions are not mounted.
The compression mechanism of claim 5, wherein said dividers (80A, 80B) are removably mounted to said ends of said second boreholes, and said dividers (80A) include spaced apart The plurality of through holes (82A) or the partition (80B) includes a single through hole (82B) at its center.
The compression mechanism according to any one of claims 1 to 3, wherein the back pressure passage is formed in the orbiting scroll end plate and extends through the orbiting scroll end plate, and the back pressure chamber formed on a second side of the orbiting scroll end plate opposite to the first side.
The compression mechanism of any one of claims 1 to 3, wherein the axial length of the expansion section is greater than the axial length of each of the narrowing sections.
The compression mechanism according to any one of claims 1 to 3, wherein each of the narrowing sections has the same flow cross-sectional area, and the fluid flow cross-sectional area of the expansion section is between the Within the range of 1.1 to 1.5 times the flow cross-sectional area of the narrowing section, or,

The narrowed sections respectively have different fluid flow cross-sectional areas, and the fluid flow cross-sectional area of the expansion section is in a range of 1.1 to 1.5 times the maximum fluid flow cross-sectional area of the narrowed section.
A scroll compressor, characterized in that the scroll compressor includes the compression mechanism according to any one of claims 1 to 9.