compressor

Abstract

The present application relates to the technical field of compressor, and specifically provides a kind of compressor.The present application is aimed at solving the problem of low space utilization of non-functional parts of crankshaft of existing compressor.For this purpose, the compressor of the present application comprises: cylinder, which is provided with compression chamber;Roller, which is arranged in the compression chamber, one end of the roller is provided with a pinion;Fixed gear, which is arranged on the flange and / or partition plate of the compressor, the fixed gear is arranged towards the cylinder, the fixed gear can be inserted into the pinion, and the pinion and the fixed gear can be rollingly engaged, which is equivalent to increasing the axial height of the fixed gear on the basis of the original axial height of the main flange or partition plate.The inner hole of the fixed gear also becomes part of the support part of the crankshaft main shaft section, and the increase of the matching length of the flange or partition plate increases the bearing area of the flange or partition plate.Under the same load condition, the contact stress on unit area is reduced, the wear risk of the flange or partition plate is reduced, and the carrying capacity and movement reliability of the shafting are improved.

Description

Technical Field

[0001] This invention relates to the field of compressor technology, and specifically provides a compressor. Background Technology

[0002] Rotary compressors are widely used in refrigeration equipment such as household air conditioners, commercial air conditioners, refrigerators, and freezers due to their high energy efficiency, compact structure, and mature manufacturing technology. The basic working principle of a rotary compressor is as follows: the motor assembly drives the crankshaft to rotate, and the eccentric part of the crankshaft drives the rollers to rotate eccentrically within the compression chamber of the cylinder. With the help of the sliding vanes, the refrigerant is drawn into the cylinder and compressed until it is compressed to a pressure exceeding the critical pressure before being discharged.

[0003] The pump body assembly of a rotary compressor is the core component of the compressor, and its structure and operational reliability directly determine the overall performance and service life of the compressor. A typical pump body assembly mainly consists of six parts: cylinder, rollers (also known as pistons), vanes, main flange (upper flange), auxiliary flange (lower flange), and crankshaft. The crankshaft runs through the entire pump body assembly; its main shaft section mates with the main flange, and its auxiliary shaft section mates with the auxiliary flange. Rollers are fitted onto the eccentric portion of the crankshaft and are positioned within the compression chamber of the cylinder. The cylinder has vane grooves, and the vanes slide within these grooves, with one end abutting against the outer wall of the rollers. The vanes, through their obstructive action, divide the cylinder interior into two periodically changing chambers: an intake chamber and a compression chamber. The main flange and auxiliary flange are located on the upper and lower sides of the cylinder, respectively, and are fixedly connected to the cylinder with screws, serving to support the crankshaft and seal the cylinder's compression chamber. The crankshaft rotates under the drive of the motor rotor, and the eccentric part drives the rollers to rotate eccentrically in the cylinder cavity, thereby compressing the refrigerant.

[0004] With the refrigeration industry's ever-increasing demands on compressor performance, miniaturization and high efficiency have become important development trends. The development direction of miniaturization and high efficiency is mainly reflected in the following two aspects: Firstly, regarding the pump body structure, reducing the radial dimensions of the crankshaft's main and auxiliary shafts (i.e., reducing the shaft diameter) decreases the friction pair area and reduces frictional power consumption, thereby improving the compressor's mechanical efficiency. Conventional rotary compressors, due to their cantilever beam or double-support crankshaft structures, typically require high crankshaft rigidity to ensure compressor reliability. Under the design trend towards smaller, more efficient models, reducing the crankshaft diameter leads to a decrease in crankshaft rigidity, which in turn affects the reliability of the shaft system's motion.

[0005] Secondly, regarding the motor structure, efficiency can be improved by increasing the stacking height of the motor core, adjusting the winding scheme, and upgrading the grade of magnetic materials (e.g., from 52SH to 56SH). However, increasing the stacking height of the core directly leads to an increase in the rotor mass. This increased rotor mass requires the crankshaft to withstand greater rotational inertial forces and gravitational loads.

[0006] The combined effect of these two miniaturization and efficiency-enhancing measures creates a prominent technical contradiction: reducing the radial dimension of the crankshaft decreases the rigidity of the shaft system, while increasing the mass of the motor rotor increases the load on the shaft system. This contradiction leads to a significant increase in the contact stress of the pump body's main flange, and simultaneously, an increase in crankshaft deflection, ultimately resulting in a decrease in shaft system reliability. As the core transmission component connecting the motor power and the pump's compression mechanism, the crankshaft's deflection directly affects the compressor's vibration, noise, and wear. Excessive crankshaft deformation can affect the thickness of the lubricating oil film, exacerbate flange wear, and may even cause rotor-stator rubbing accidents.

[0007] To address the decline in shaft system reliability, existing technologies typically employ two strategies: one is to increase the crankshaft diameter to improve its rigidity; the other is to increase the axial height (i.e., flange mating length) of the main flange and / or auxiliary flange to increase the flange bearing area and reduce contact stress. However, both strategies face difficulties under the design goal of miniaturization and high efficiency: increasing the crankshaft diameter increases the friction pair area, leading to reduced mechanical efficiency, which contradicts the goal of miniaturization and high efficiency; increasing the flange height increases the overall height of the pump body, which is detrimental to compressor miniaturization.

[0008] Further analysis of existing crankshaft structures reveals that the actual mating height between the crankshaft eccentric portion and the rollers is typically only 0.5 to 0.8 times the cylinder height. In other words, 20% to 50% of the axial length of the crankshaft eccentric portion does not participate in the friction pair mating between the eccentric portion and the rollers. These non-matting stepped portions (i.e., the stepped areas at both ends of the eccentric portion) primarily connect the main shaft and the auxiliary shaft, belonging to non-functional parts of the crankshaft and not serving as functional load-bearing parts of the shaft system. This portion of the height space is not effectively utilized in existing technologies.

[0009] From the perspective of shaft system stress analysis, the crankshaft with a double-support structure has the following stress distribution relationship between its main shaft and secondary shaft: in: F bp Total load on the eccentric part of the shaft system (i.e., the total load of the rollers acting on the eccentric part of the crankshaft). F sb Total load on the secondary shaft (load borne by the secondary flange) F mb Total spindle load (load borne by the main flange) X Distance between the center of the secondary shaft mating section and the center of the eccentric shaft. L : The distance between the center of the auxiliary shaft mating section and the center of the main shaft mating section (i.e., the support span between the main flange and the auxiliary flange). From the above force formula, it can be seen that when the radial dimensions of the crankshaft's main shaft and auxiliary shaft decrease and the mass of the motor rotor increases, the total load on the eccentric part of the shaft system... F bp Increase, and the support span between the main flange and the secondary flange increases. L and the distance from the center of the secondary shaft mating section to the center of the eccentric shaft. X The load on the spindle did not increase accordingly, which directly led to a decrease in the total spindle load. F mb and total load of the secondary shaft F sb The increase in flange contact stress, without a corresponding increase in the flange's bearing area, inevitably leads to an increase in flange contact stress. Simultaneously, the bending moment on the crankshaft increases, resulting in a corresponding increase in crankshaft deflection. The combined increase in flange contact stress and crankshaft deflection leads to a decrease in the reliability of the shaft system's motion.

[0010] To address the aforementioned technical problems, some improvements have been proposed in the existing technology. For example, one solution proposes adding a motor-side support flange to the upper end of the motor to support the crankshaft (i.e., double-support technology) to reduce crankshaft deformation, allowing the crankshaft to withstand greater compressed gas force and motor magnetic pull even with a smaller shaft diameter. However, the double-support technology increases the number of flanges and structural complexity, negatively impacting the manufacturability and cost of the compressor. Another solution proposes setting a friction-reducing seal on the end face of the flange inner ring, which abuts against the flange to reduce wear on the flange inner ring. Yet another solution uses a tungsten disulfide coating on the friction pair surface to reduce the coefficient of friction and improve energy efficiency. However, none of these solutions effectively solve the problem of low space utilization in the non-functional parts of the crankshaft, nor do they fundamentally improve the load distribution of the shaft system.

[0011] Therefore, there is an urgent need for a compressor to solve the above-mentioned technical problems. Summary of the Invention

[0012] The present invention aims to solve the above-mentioned technical problems, namely, to solve the problem of low space utilization of non-functional parts of existing compressor crankshafts.

[0013] In a first aspect, the present invention provides a compressor comprising: A cylinder, which has a compression chamber; A roller is disposed inside the compression chamber, and a moving gear is disposed on the inner side of one end of the roller; A fixed gear is disposed on the flange and / or partition of the compressor, the fixed gear is positioned toward the cylinder, the fixed gear can extend into the driven gear, and the driven gear and the fixed gear can roll and mesh.

[0014] In a specific embodiment of the compressor described above, the diameter of the moving gear is larger than the diameter of the inner bore of the roller.

[0015] In a specific embodiment of the compressor described above, the fixed gear is mounted on the main flange of the cylinder near the motor end.

[0016] In a specific embodiment of the compressor described above, the fixed gear is disposed on the secondary flange at the end of the cylinder away from the motor.

[0017] In a specific embodiment of the compressor described above, the fixed gear is disposed on the partition plate.

[0018] In a specific embodiment of the compressor described above, the fixed gear and the flange or the partition are integrally formed.

[0019] In the specific embodiment of the compressor described above, the moving gear and the roller are integrally formed.

[0020] In the specific embodiment of the compressor described above, both ends of the roller are provided with the moving gear, and the flanges or partitions on both sides of the cylinder are provided with the fixed gear.

[0021] In a specific embodiment of the compressor described above, the compressor includes: A crankshaft, which passes through the roller, the flange, and the fixed gear, and has a drive unit that engages with the portion of the roller not equipped with the moving gear, allows the crankshaft to drive the roller to rotate via the drive unit; and / or The cylinder is provided with a vane groove, and the compressor further includes a vane and an elastic element. The vane is slidably disposed in the vane groove, and the elastic element drives the first end of the vane to abut against the outer wall of the roller; and / or The cylinder is provided with a receiving hole, and the elastic element is disposed in the receiving hole, with one end of the elastic element abutting against the second end of the slide plate.

[0022] In a specific embodiment of the compressor described above, the compressor further includes a rotor and a stator, the rotor being disposed on the crankshaft and the stator being disposed around the rotor.

[0023] The beneficial effects of this invention are as follows: The protruding fixed gear extends into the roller, effectively increasing the axial height of the fixed gear on top of the original axial height of the main flange or partition. The inner bore of the fixed gear also forms part of the support portion of the crankshaft main section, thus increasing the mating length between the flange or partition and the crankshaft main section. This increased mating length increases the bearing area of ​​the flange or partition, reducing the contact stress per unit area under the same load conditions. This effectively reduces the wear risk of the flange or partition, improving the load-bearing capacity and operational reliability of the shaft system.

[0024] Secondly, because the fixed gear extends into the roller, utilizing the space inside the roller, the increase in the flange or diaphragm mating length does not increase the overall height of the pump body structure. In other words, this invention achieves an increase in the effective mating length of the flange or diaphragm without increasing the overall height of the pump body, thus balancing the improvement of shaft system reliability and the need for compressor miniaturization.

[0025] Third, the meshing of the moving gear and the fixed gear establishes a mechanical constraint relationship between the roller and the main flange, which improves the stability of the roller's rotational motion and reduces the axial movement and radial runout of the roller during operation.

[0026] Fourth, through the transmission action of gear meshing, the power of the crankshaft can be transmitted to the rollers more efficiently, reducing energy loss in the power transmission process and improving the transmission efficiency of the shaft system. Attached Figure Description

[0028] The preferred embodiments of the present invention are described below with reference to the accompanying drawings, in which: Figure 1 This is a schematic diagram of the compressor provided in Embodiment 1 of the present invention; Figure 2 This is a cross-sectional view of the compressor provided in Embodiment 1 of the present invention. Figure 1 ; Figure 3 This is a cross-sectional view of the compressor provided in Embodiment 1 of the present invention. Figure 2 ; Figure 4 This is a schematic diagram of the auxiliary flange of the compressor provided in Embodiment 1 of the present invention; Figure 5 This is a schematic diagram of the structure of the rollers of the compressor provided in Embodiment 1 of the present invention.

[0029] List of reference numerals in the attached diagram: 1. Cylinder; 2. Roller; 21. Drive gear; 3. Secondary flange; 31. Fixed gear; 4. Main flange; 5. Crankshaft; 6. Sliding vane. Detailed Implementation

[0031] Preferred embodiments of the present invention will now be described with reference to the accompanying drawings. Those skilled in the art should understand that these embodiments are merely illustrative of the technical principles of the present invention and are not intended to limit the scope of protection of the present invention.

[0032] It should be noted that in the description of this invention, terms such as "upper," "lower," "left," "right," "inner," and "outer," indicating directional or positional relationships, are based on the directional or positional relationships shown in the accompanying drawings. These are merely for ease of description and do not indicate or imply that the device or element must have a specific orientation, or be constructed and operated in a specific orientation; therefore, they should not be construed as limitations on this invention. Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance.

[0033] Furthermore, it should be noted that, in the description of this invention, unless otherwise explicitly specified and limited, the terms "installation," "setting," and "connection" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a direct connection, an indirect connection through an intermediate medium, or a connection within two components. Those skilled in the art can understand the specific meaning of the above terms in this invention according to the specific circumstances.

[0034] In order to solve the problems mentioned in the background art, the present invention provides a compressor, and the compressor of the present invention will be described in detail below with reference to several embodiments.

[0035] Implementation Method 1 like Figure 1-5 As shown, this embodiment provides a compressor, including a cylinder 1, rollers 2, a crankshaft 5, a flange, and vanes 6. The cylinder 1 is generally an annular cylindrical structure, with a cylindrical compression chamber inside. The rollers 2 are rotatably disposed within the compression chamber. The cylinder 1 is provided with a vane 6 groove, which extends radially from the outer wall of the cylinder 1 to the compression chamber. The cylinder 1 is also provided with a receiving hole located at the radially outer end of the vane 6 groove for accommodating an elastic element.

[0036] The elastic element is used to drive the first end of the slide 6 to abut against the outer wall of the roller 2; the elastic element is specifically a compression spring, and two notches are provided on the second end of the slide 6, with one end of the spring extending into the notch.

[0037] The compressor also includes a motor assembly, which consists of a rotor and a stator. The rotor is fixedly mounted on the upper end of the crankshaft 5, and the stator is arranged around the rotor and fixedly mounted on the inner wall of the compressor housing. When the stator is energized, it generates a rotating magnetic field, which drives the rotor to rotate. The rotor drives the crankshaft 5 to rotate, which in turn drives the rollers 2 to perform eccentric rotational motion within the compression chamber of the cylinder 1.

[0038] In this embodiment, when the compressor includes only one cylinder 1, there are two flanges on both sides of the cylinder 1; namely, a main flange 4 and a secondary flange 3. The main flange 4 (also known as the upper flange) is located at the upper end (i.e., the axial side) of the cylinder 1, used to close the upper opening of the compression chamber of the cylinder 1, and also serves as the main shaft support for the crankshaft 5. The main flange 4 has a disc-shaped structure, with a flange hole in its center. The flange hole extends axially through the main flange 4 for the main shaft section of the crankshaft 5 to pass through. The main flange 4 is fixedly connected to the cylinder 1 by fasteners such as screws. It can also be connected to the secondary flange 3, etc., by screws.

[0039] The secondary flange 3 (also known as the lower flange) is located at the lower end of cylinder 1 (i.e., on the other side of the axial direction) to seal the lower opening of the compression chamber of cylinder 1, and also serves as a support for the secondary shaft of crankshaft 5. The structure of the secondary flange 3 is similar to that of the main flange 4, with a flange hole in its center for the secondary shaft section of crankshaft 5 to pass through. The secondary flange 3 is fixedly connected to cylinder 1 by screws or other fasteners. It can also be connected to the main flange 4 by screws or other fasteners.

[0040] The crankshaft 5 is mounted on the main flange 4, rollers 2, and auxiliary flange 3. Along the axial direction from top to bottom, the crankshaft 5 comprises a main shaft section, an eccentric section (drive section), and an auxiliary shaft section. The main shaft section mates with the flange holes of the main flange 4, and the auxiliary shaft section mates with the flange holes of the auxiliary flange 3. The eccentric section is located between the main shaft section and the auxiliary shaft section, and there is a certain eccentricity between the central axis of the eccentric section and the rotational central axis of the crankshaft 5. Rollers 2 are fitted onto the eccentric section, and the inner hole of rollers 2 slides with the outer circumferential surface of the eccentric section. When the crankshaft 5 rotates, the eccentric section drives the rollers 2 to perform eccentric rotational motion within the compression chamber of the cylinder 1 to compress the refrigerant.

[0041] The slide plate 6 is a long, strip-shaped structure that is slidably disposed within the slide plate 6 groove of the cylinder 1. The first end (radially inner end) of the slide plate 6 extends into the compression chamber to abut against the outer wall of the roller 2. The second end (radially outer end) of the slide plate 6 abuts against one end of an elastic element disposed within a receiving hole. The other end of the elastic element abuts against the bottom of the receiving hole. The elastic element constantly applies an elastic force towards the roller 2 to the slide plate 6, driving the first end of the slide plate 6 to remain in contact with the outer wall of the roller 2. Through the blocking effect of the slide plate 6, the compression chamber of the cylinder 1 is divided into two periodically changing chambers: an intake chamber and a compression chamber.

[0042] A fixed gear 31 (external gear) protrudes from the side of the auxiliary flange 3 facing the cylinder 1 (i.e., the upper end face). The fixed gear 31 has a ring-shaped structure with external teeth on its outer circumference. The central axis of the fixed gear 31 is coaxial with the central axis of the auxiliary flange 3 and the rotation center axis of the crankshaft 5. The fixed gear 31 protrudes upward from the upper end face of the auxiliary flange 3 and extends into the interior of the roller 2.

[0043] A movable gear 21 (internal gear) is provided on the lower inner side of the roller 2 (i.e., the lower end of the inner hole of the roller 2). The movable gear 21 has a ring-shaped structure, and internal teeth are provided on its inner circumferential surface. The fixed gear 31 extends into the interior of the movable gear 21. The central axis of the movable gear 21 is coaxial with the central axis of the roller 2. The movable gear 21 is located at the lower end of the inner hole of the roller 2 and does not protrude from the lower end face of the roller 2.

[0044] Some of the external teeth of the fixed gear 31 mesh with some of the internal teeth of the moving gear 21. When the crankshaft 5 drives the roller 2 to rotate eccentrically in the compression chamber of the cylinder 1, the moving gear 21 of the roller 2 and the fixed gear 31 of the auxiliary flange 3 maintain a rolling meshing state.

[0045] In this embodiment, the fixed gear 31 and the auxiliary flange 3 adopt an integral structure, that is, the fixed gear 31 and the auxiliary flange 3 are made by integral molding; the integral structure has the advantages of simple structure, high strength, convenient assembly and good coaxiality.

[0046] Regarding the fixing method of the fixed gear 31 and the auxiliary flange 3, it should be noted that although an integral structure is used in this embodiment, this is not a limitation of the present invention. Without departing from the principle of the present invention, in other embodiments, a split design can also be adopted, and then fixed by welding or screw connection.

[0047] The moving gear 21 and the roller 2 adopt an integrated structure, that is, the moving gear 21 and the roller 2 are made by integral molding; the integrated structure has the advantages of simple structure, high strength, convenient assembly and good coaxiality.

[0048] Regarding the fixing method of the fixed gear 31 and the auxiliary flange 3, it should be noted that although an integral structure is used in this embodiment, this is not a limitation of the present invention. Without departing from the principle of the present invention, in other embodiments, a split design can also be adopted, and then fixed by welding or screw connection.

[0049] In this embodiment, the compressor also includes a motor assembly, which comprises a rotor and a stator. The rotor is fixedly mounted on the upper end of the crankshaft 5 (the upper end of the main shaft section), and the stator is arranged around the rotor and fixedly mounted on the inner wall of the compressor housing. When the stator is energized, it generates a rotating magnetic field, which drives the rotor to rotate. The rotor drives the crankshaft 5 to rotate, which in turn drives the rollers 2 to perform eccentric rotational motion within the compression chamber of the cylinder 1.

[0050] The working principle of this implementation method is as follows: When the compressor is working, the stator is energized to generate a rotating magnetic field, which drives the rotor to rotate. The rotor drives the crankshaft 5 to rotate around its central axis. During the rotation of the crankshaft 5, the eccentric part drives the roller 2 sleeved on it to rotate eccentrically within the compression chamber of the cylinder 1. During the eccentric rotation of the roller 2, its outer wall remains in contact with the first end of the sliding vane 6, which divides the compression chamber into an intake chamber and a compression chamber. As the roller 2 rotates eccentrically, the volume of the intake chamber periodically increases, drawing refrigerant into the compression chamber; the volume of the compression chamber periodically decreases, compressing the refrigerant until the pressure exceeds the critical pressure and it is discharged.

[0051] During the eccentric rotation of roller 2, the moving gear 21 on the inner side of the upper end of roller 2 meshes with the fixed gear 31 on the lower end face of the auxiliary flange 3. Since the fixed gear 31 is fixedly mounted on the auxiliary flange 3 (which is fixedly connected to the cylinder 1 and does not rotate with the crankshaft 5), the moving gear 21 moves together with roller 2, creating a relative rolling motion between the moving gear 21 and the fixed gear 31. This gear meshing relationship brings the following beneficial effects: First, the fixed gear 31 protrudes upward from the upper end face of the secondary flange 3 and extends into the interior of the roller 2, effectively increasing the axial height of the fixed gear 31 on top of the original axial height of the secondary flange 3. The inner bore of the fixed gear 31 also forms part of the support portion of the crankshaft 5 main shaft section, thus increasing the mating length between the secondary flange 3 and the crankshaft 5 main shaft section. This increased flange mating length increases the flange's load-bearing area, reducing the contact stress per unit area under the same load conditions, thereby effectively reducing the risk of flange wear and improving the bearing capacity and operational reliability of the shaft system.

[0052] Secondly, since the fixed gear 31 extends into the roller 2, utilizing the space inside the roller 2, the increase in the mating length of the secondary flange 3 does not increase the overall height of the pump body structure. In other words, this invention achieves an increase in the effective mating length of the flange without increasing the overall height of the pump body, thus balancing the improvement of shaft system reliability and the need for compressor miniaturization.

[0053] Third, the meshing of the moving gear 21 and the fixed gear 31 establishes a mechanical constraint relationship between the roller 2 and the sub-flange 3, which improves the stability of the rotational motion of the roller 2 and reduces the axial movement and radial runout of the roller 2 during operation.

[0054] Fourth, through the transmission action of gear meshing, the power of crankshaft 5 can be transmitted to roller 2 more efficiently, reducing energy loss in the power transmission process and improving the transmission efficiency of the shaft system.

[0055] Implementation Method 2 The compressor provided in Embodiment 2 of the present invention differs from that in Embodiment 1 in that: a fixed gear 31 is provided on the main flange 4, and a moving gear 21 is provided on the upper end of the roller 2.

[0056] Implementation Method 3 The compressor provided in Embodiment 3 of the present invention differs from that in Embodiment 1 in that: both the main flange 4 and the auxiliary flange 3 are provided with fixed gears 31, and both ends of the roller 2 are provided with moving gears 21.

[0057] Specifically, a fixed gear 31 (first fixed gear 31) protrudes from the side (lower end face) of the main flange 4 facing the cylinder 1. A fixed gear 31 (second fixed gear 31) protrudes from the side (upper end face) of the auxiliary flange 3 facing the cylinder 1. A moving gear 21 (first moving gear 21) is provided on the inner side of the upper end of the roller 2, and a moving gear 21 (second moving gear 21) is provided on the inner side of the lower end of the roller 2. The fixed gear 31 of the main flange 4 meshes with the moving gear 21 at the upper end of the roller 2, and the fixed gear 31 of the auxiliary flange 3 meshes with the moving gear 21 at the lower end of the roller 2.

[0058] The first fixed gear 31 and the main flange 4 can be integrally formed or designed separately and then connected and fixed; the second fixed gear 31 and the auxiliary flange 3 can be integrally formed or designed separately and then connected and fixed.

[0059] The first moving gear 21 and the roller 2 can be integrally formed or designed separately and then connected and fixed; the second moving gear 21 and the roller 2 can be integrally formed or designed separately and then connected and fixed.

[0060] In this embodiment, both the main flange 4 and the auxiliary flange 3 extend into the roller 2 via the fixed gear 31, simultaneously increasing the mating length between the flange and the crankshaft 5 on both the upper and lower sides of the cylinder 1. Compared to embodiment one, this embodiment further increases the total bearing area of ​​the flange, further reduces the flange contact stress, and further improves the bearing capacity and motion reliability of the shaft system.

[0061] Meanwhile, both ends of the roller 2 are meshed with the fixed gear 31 through the moving gear 21, and the roller 2 is constrained by the gear meshing at both ends in the axial direction, which further improves the stability of the rotational motion.

[0062] The other structures, working principles, and beneficial effects of this embodiment are similar to those of Embodiment 1, and will not be repeated here.

[0063] Implementation Method 4 The compressor provided in Embodiment 4 of the present invention differs from that in Embodiment 1 in that the number of cylinders 1 is two, and a partition is provided between the two cylinders 1.

[0064] Both the main flange 4 and the auxiliary flange 3 are equipped with fixed gears 31, and the roller 2 near the main flange 4 is equipped with a moving gear 21 on the side of the roller 2 near the main flange 4; the roller 2 near the auxiliary flange 3 is equipped with a moving gear 21 on the side of the roller 2 near the auxiliary flange 3.

[0065] The crankshaft 5 has two eccentric parts, which are respectively configured to cooperate with two rollers 2.

[0066] Implementation Method 5 The compressor provided in Embodiment 5 of the present invention differs from that in Embodiment 4 in that: both the main flange 4 and the partition plate are provided with fixed gears 31, the fixed gears 31 on the main flange 4 and the partition plate face to the same side, and the moving gears 21 on the two rollers 2 are also arranged facing one side of the main flange 4.

[0067] Implementation Method Six The compressor provided in Embodiment Six of the present invention differs from that in Embodiment Four in that: both the secondary flange 3 and the partition plate are provided with fixed gears 31, the fixed gears 31 on the secondary flange 3 and the partition plate face to the same side, and the moving gears 21 on the two rollers 2 are also arranged facing one side of the secondary flange 3.

[0068] Implementation Method Seven The compressor provided in Embodiment Seven of the present invention differs from that in Embodiment Four in that: fixed gears 31 are provided on both sides of the partition, and the moving gears 21 on the two rollers 2 are also arranged facing one side of the partition.

[0069] Implementation Method Eight The compressor provided in Embodiment 8 of the present invention differs from that in Embodiment 1 in that: the number of cylinders 1 is multiple, and a partition is provided between two adjacent cylinders 1.

[0070] Each roller 2 is provided with at least one moving gear 21, and the fixed gear 31 is correspondingly provided on the flange or partition; that is, the moving gear 21 and the fixed gear 31 are arranged in a group.

[0071] The crankshaft 5 is provided with multiple eccentric parts, which are respectively set one-to-one with multiple rollers 2.

[0072] The technical solution of the present invention has been described above with reference to the preferred embodiments shown in the accompanying drawings. However, it will be readily understood by those skilled in the art that the scope of protection of the present invention is obviously not limited to these specific embodiments. Without departing from the principles of the present invention, those skilled in the art can make equivalent changes or substitutions to the relevant technical features, and the technical solutions after such changes or substitutions will all fall within the scope of protection of the present invention.

Claims

1. A compressor, characterized in that, The compressor includes: Cylinder (1), which is provided with a compression chamber; A roller (2) is disposed in the compression chamber, and a moving gear (21) is disposed on the inner side of one end of the roller (2). A fixed gear (31) is disposed on the flange and / or partition of the compressor, the fixed gear (31) is disposed toward the cylinder (1), the fixed gear (31) can extend into the moving gear (21), and the moving gear (21) and the fixed gear (31) can roll and mesh.

2. The compressor according to claim 1, characterized in that, The diameter of the moving gear (21) is larger than the diameter of the inner hole of the roller (2).

3. The compressor according to claim 1, characterized in that, The fixed gear (31) is mounted on the main flange (4) of the cylinder (1) near the motor end.

4. The compressor according to claim 1, characterized in that, The fixed gear (31) is mounted on the auxiliary flange (3) at the end of the cylinder (1) away from the motor.

5. The compressor according to claim 1, characterized in that, The fixed gear (31) is disposed on the partition plate.

6. The compressor according to any one of claims 1-5, characterized in that, The fixed gear (31) and the flange or the partition are integrally formed.

7. The compressor according to any one of claims 1-5, characterized in that, The moving gear (21) and the roller (2) are integrally formed.

8. The compressor according to claim 1, characterized in that, Both ends of the roller (2) are provided with the moving gear (21), and the flanges or partitions on both sides of the cylinder (1) are provided with the fixed gear (31).

9. The compressor according to claim 1, characterized in that, The compressor includes: A crankshaft (5) is provided, which passes through the roller (2), the flange, and the fixed gear (31). A drive unit is provided on the crankshaft (5), which cooperates with the part of the roller (2) where the moving gear (21) is not provided. The crankshaft (5) can drive the roller (2) to rotate through the drive unit; and / or The cylinder (1) is provided with a sliding vane (6) groove, and the compressor further includes a sliding vane (6) and an elastic element. The sliding vane (6) is slidably disposed in the sliding vane (6) groove, and the elastic element drives the first end of the sliding vane (6) to abut against the outer wall of the roller (2); and / or The cylinder (1) is provided with a receiving hole, and the elastic element is disposed in the receiving hole. One end of the elastic element abuts against the second end of the slide (6).

10. The compressor according to claim 9, characterized in that, The compressor also includes a rotor and a stator, the rotor being disposed on the crankshaft (5) and the stator being disposed around the rotor.

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