A sliding vane transmission mechanism, pump body assembly and compressor

Abstract

The application discloses a sliding vane transmission mechanism, a pump body assembly and a compressor, and relates to the technical field of compressors. The sliding vane transmission mechanism comprises at least two sliding vanes, and adjacent two sliding vanes are arranged in an up-down mode; a transmission lever is in contact with the tail portions of the adjacent two sliding vanes; when one of the adjacent two sliding vanes is forced to move, the transmission lever drives the other sliding vane to move, and the moving directions of the adjacent two sliding vanes are opposite. The application utilizes the lever principle to transmit the driving force required by the sliding vane movement, ensures that the sliding vane and the roller are always in the abutting state, and has the advantages of faster response speed compared with the time delay and hysteresis problems existing in the traditional spring structure, so that the sliding vane and the roller are always closely attached, and the problem of jumping of the sliding vane in the running process is avoided.

Description

Technical Field

[0001] This invention relates to the field of compressor technology, and in particular to a vane drive mechanism, a pump assembly, and a compressor. Background Technology

[0002] As the core component of refrigeration and air conditioning, the compressor's performance directly affects the air conditioner's cooling capacity, energy efficiency ratio, and noise level. With the improvement of living standards, high efficiency and low noise in air conditioning compressors have become the main trends in industry development. The vane, as a significant source of frictional power consumption and mechanical noise, is currently used in rotary compressors for air conditioning. The vane is forced to maintain contact between the head and the roller through the force of the tail spring and the unbalanced gas force between the head and tail.

[0003] By using spring force and unbalanced gas force to force the vane head to remain in contact with the roller, the following problems arise: During the initial compressor startup, the end of the exhaust phase, or high-frequency operation, the vane is prone to jumping, causing it to detach from the roller. In the initial drive phase, before the pressure difference between the intake and exhaust chambers is established, the vane may jump due to insufficient pressure difference at both ends, leading to abnormal wear of the head. At the end of the exhaust phase, the cylinder exhaust pressure rises sharply, reducing the pressure difference at both ends of the vane, which may prevent the vane from tightly adhering to the roller surface. Under high-frequency operation, the reciprocating speed of the vane in the vane groove increases, requiring a larger pressure difference; if the actual pressure difference is insufficient, this will also cause the vane to jump.

[0004] When the vane bounces, the vane and roller repeatedly cycle through contact-disengagement-contact, causing collisions between moving parts and generating significant operating noise. Furthermore, vane bounce leads to abnormal wear on the head, reducing operational reliability; disengagement between the vane and roller can also cause refrigerant leakage, degrading overall machine performance. Summary of the Invention

[0005] The purpose of this invention is to overcome the shortcomings of the prior art and provide a vane drive mechanism, a pump body assembly, and a compressor, which aims to solve the problem of vane jumping during compressor operation.

[0006] To achieve the above objectives, the present invention adopts the following technical solution:

[0007] In a first aspect, the present invention provides a sliding vane transmission mechanism, comprising:

[0008] At least two sliders are arranged vertically on adjacent sliders;

[0009] The transmission lever contacts the tail ends of the two adjacent sliding plates;

[0010] When one of the two adjacent sliders is subjected to force and moves, the transmission lever drives the other slider to move, and the two adjacent sliders move in opposite directions.

[0011] Furthermore, the transmission lever includes a first contact portion, a second contact portion, and a lever shaft, with the lever shaft disposed between the first contact portion and the second contact portion, and the first contact portion and the second contact portion respectively contacting two adjacent slides.

[0012] Furthermore, the length of the transmission lever satisfies: L>H / sin(α), where α is the angle between the direction of the transmission lever's working limit position and the horizontal direction, H is the vertical height from the position of the lever shaft to the contact position between the transmission lever and the slider, and L is the length of the transmission lever.

[0013] Furthermore, the transmission lever is made of an elastic material.

[0014] Furthermore, it also includes a partition plate, which is disposed between two adjacent sliding plates, and the transmission lever is disposed on the partition plate.

[0015] Furthermore, the partition plate is provided with a lever mounting groove, and the transmission lever is rotatably disposed in the lever mounting groove.

[0016] Furthermore, the position where the tail of the slider contacts the transmission lever is an arc shape or a sharp angle shape.

[0017] Secondly, the present invention also provides a pump body assembly, including the above-mentioned vane transmission mechanism, crankshaft, at least two cylinders and at least two rollers, each of the cylinders having a working chamber and a vane groove, the crankshaft passing through the working chamber, the rollers being sleeved on the crankshaft and located in the working chamber, the vane being slidably disposed in the vane groove, and the head of the vane abutting against the outer surface of the roller.

[0018] Furthermore, the crankshaft includes a rotating shaft and at least two eccentric portions disposed on the outer periphery of the rotating shaft. All the eccentric portions have the same eccentricity, and adjacent eccentric portions are distributed on opposite sides of the crankshaft. The eccentric portions abut against the inner surface of the roller.

[0019] Thirdly, the present invention also provides a compressor including the pump body assembly described above.

[0020] The advantages of this invention compared to existing technologies are as follows: A sliding vane transmission mechanism includes at least two sliding vanes, with adjacent sliding vanes arranged vertically; a transmission lever contacts the tails of the two adjacent sliding vanes; when one of the two adjacent sliding vanes is subjected to force and moves, the transmission lever drives the other sliding vane to move, and the two adjacent sliding vanes move in opposite directions. This invention utilizes the lever principle to transmit the driving force required for the sliding vane movement, ensuring that the sliding vane and roller are always in contact. Compared to the delay and hysteresis problems of traditional spring structures, the response speed is faster, thus ensuring that the sliding vane and roller are always in close contact and avoiding the problem of sliding vane jumping during operation.

[0021] The above description is merely an overview of the technical solution of the present invention. In order to better understand the technical means of the present invention, it can be implemented according to the contents of the specification. In order to make the above and other objectives, features and advantages of the present invention more obvious and understandable, preferred embodiments are described in detail below. Attached Figure Description

[0022] To more clearly illustrate the technical solutions of the embodiments of the present invention, the drawings used in the following description of the embodiments will be briefly introduced. Obviously, the drawings described below are some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0023] Figure 1 A schematic diagram of the structure of a pump body assembly provided in a specific embodiment of the present invention;

[0024] Figure 2 A cross-sectional view of a pump body assembly provided for a specific embodiment of the present invention;

[0025] Figure 3 A schematic diagram of the transmission lever provided in a specific embodiment of the present invention;

[0026] Figure 4 A schematic diagram of the partition structure provided in a specific embodiment of the present invention;

[0027] Figure 5 A schematic diagram of the slider provided in a specific embodiment of the present invention;

[0028] Figure 6 A schematic diagram of the crankshaft structure provided in a specific embodiment of the present invention;

[0029] Figure 7 This is a schematic diagram of the motion of the transmission lever in a specific embodiment of the present invention;

[0030] Figure 8 This is a schematic diagram of the structure of a compressor according to a specific embodiment of the present invention;

[0031] Figure 9 This is a schematic diagram showing the relationship between the various components of the compressor.

[0032] Figure Labels

[0033] 1. Sliding plate; 11. Tail end of sliding plate; 12. Head end of sliding plate; 2. Transmission lever; 21. Lever shaft; 22. First contact part; 23. Second contact part; 3. Partition plate; 31. Lever mounting groove; 32. Shaft hole; 4. Crankshaft; 41. Rotating shaft; 42. Eccentric part; 5. Roller. Detailed Implementation

[0034] The technical solution of the present invention will be clearly and completely described below with reference to specific embodiments. Obviously, the described embodiments are only some, not all, of the embodiments of the present invention. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0035] In the description of this invention, it should be understood that the terms "center," "longitudinal," "lateral," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "clockwise," "counterclockwise," "axial," "radial," and "circumferential" indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are used only for the convenience of describing this invention and simplifying the description, and do not indicate or imply that the device or element referred to 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.

[0036] Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one of that feature. In the description of this invention, "a plurality of" means at least two, such as two, three, etc., unless otherwise explicitly specified.

[0037] In this invention, unless otherwise explicitly specified and limited, the terms "installation," "connection," "linking," and "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components, unless otherwise explicitly limited. Those skilled in the art can understand the specific meaning of the above terms in this invention according to the specific circumstances.

[0038] In this invention, unless otherwise explicitly specified and limited, "above" or "below" the second feature can mean that the first feature is in direct contact with the second feature, or that the first feature is in indirect contact with the second feature through an intermediate medium. Furthermore, "above," "over," and "on top" of the second feature can mean that the first feature is directly above or diagonally above the second feature, or simply that the first feature is at a higher horizontal level than the second feature. "Below," "below," and "under" the second feature can mean that the first feature is directly below or diagonally below the second feature, or simply that the first feature is at a lower horizontal level than the second feature.

[0039] It should be noted that when an element is referred to as being "fixed to" or "set on" another element, it can be directly on the other element or there may be an intervening element. When an element is considered to be "connected to" another element, it can be directly connected to the other element or there may be an intervening element. The terms "vertical," "horizontal," "upper," "lower," "left," "right," and similar expressions used herein are for illustrative purposes only and do not represent the only possible implementation.

[0040] As the core component of refrigeration and air conditioning, the compressor's performance directly affects the air conditioner's cooling capacity, energy efficiency ratio, and noise. With the improvement of living standards, high efficiency and low noise in air conditioning compressors have become the main trends in industry development. The vane 1, as a significant source of frictional power consumption and mechanical noise, is currently used in rotary compressors for air conditioning. The vane 1 is forced to maintain contact between the head 12 of the vane and the roller 5 through the force of the tail spring and the unbalanced gas force between the head and tail.

[0041] The method of forcing the head 12 of the vane to remain in contact with the roller 5 by using spring force and unbalanced gas force presents the following problems: During the initial startup of the compressor, at the end of the exhaust phase, or during high-frequency operation, the vane 1 is prone to jumping, causing it to separate from the roller 5. In the initial drive phase, before the pressure difference between the intake and exhaust chambers is established, the vane 1 may jump due to insufficient pressure difference at both ends, leading to abnormal wear of the head. At the end of the exhaust phase, the cylinder exhaust pressure rises sharply, reducing the pressure difference at both ends of the vane 1, which may prevent the vane 1 from tightly adhering to the surface of the roller 5. During high-frequency operation, the reciprocating speed of the vane 1 in the vane groove increases, requiring a larger pressure difference; if the actual pressure difference is insufficient, this will also cause the vane 1 to jump.

[0042] When the slide plate 1 jumps, the slide plate 1 and the roller 5 repeatedly cycle through contact-disengagement-contact, causing collisions between moving parts and generating significant operating noise. Furthermore, the jumping of the slide plate 1 causes abnormal wear on the head, reducing operational reliability; the disengagement of the slide plate 1 from the roller 5 can also cause refrigerant leakage, reducing overall machine performance. Therefore, this invention is proposed, and specific embodiments are described below.

[0043] This invention is applicable to compressors with two or more cylinders.

[0044] like Figures 1 to 9 As shown, this embodiment of the invention provides a pump body assembly, including a vane transmission mechanism, a crankshaft 4, at least two cylinders and at least two rollers 5. Each cylinder is provided with a working chamber and a vane groove. The crankshaft 4 passes through the working chamber, and the rollers 5 are sleeved on the crankshaft 4 and located in the working chamber. The vane transmission mechanism includes a transmission lever 2 and at least two vanes 1. The transmission lever 2 contacts the tails 11 of two adjacent vanes. When one of the two adjacent vanes 1 is subjected to force and moves, the transmission lever 2 drives the other vane 1 to move. The movement directions of the two adjacent vanes 1 are opposite. The two adjacent vanes 1 are arranged vertically. The vanes 1 are slidably arranged in the vane groove, and the head 12 of the vane abuts against the outer surface of the roller 5.

[0045] Specifically, taking a two-cylinder compressor as an example, it includes two cylinders, each with an independent working chamber and a vane groove. The working chamber provides space for the movement of the roller 5 and the crankshaft 4, while the vane groove is used to accommodate the vane 1 and limit its movement trajectory. The crankshaft 4 passes through the working chambers of the two cylinders, and the roller 5 is sleeved on the crankshaft 4 and located in the working chamber, and can perform circular motion under the drive of the crankshaft 4.

[0046] Two slide plates 1 are slidably arranged in the slide plate slots of the two cylinders, the number of slide plates 1 corresponding to the number of cylinders, and adjacent slide plates 1 are arranged vertically. The head 12 of the slide plate can tightly abut against the outer surface of the roller 5; the tail 11 of the slide plate is used to contact the transmission lever 2.

[0047] When one of the sliders 1 is subjected to force and moves, the slider 1 moves in a certain direction under the push of the roller 5, and the force of the tail 11 of the slider in the transmission lever 2 drives the other slider 1 to move in the opposite direction.

[0048] By connecting adjacent sliding vanes 1 using a lever transmission method, the consistency of vane 1 movement is ensured, effectively overcoming the problem of vane 1 jumping due to insufficient pressure difference and excessive frequency in traditional structures. In the initial stage of compressor startup, the end of exhaust phase, or high-frequency operation, vane 1 in traditional structures is prone to detaching from roller 5. However, in this solution, the transmission lever 2 can transmit power in a timely manner, keeping vane 1 in contact with roller 5 at all times, avoiding collisions of moving parts caused by vane 1 jumping, significantly reducing operating noise, and improving the stability and reliability of compressor operation. Simultaneously, the lever transmission structure prevents vane 1 from detaching from roller 5, reducing the possibility of refrigerant leakage. Traditional spring structures have delay and hysteresis problems, which cannot guarantee a tight fit between vane 1 and roller 5 under certain operating conditions, leading to refrigerant leakage and reducing overall machine performance. The lever transmission of this invention has a fast response speed, ensuring that vane 1 and roller 5 are always in tight contact, effectively preventing refrigerant leakage and improving the compressor's energy efficiency ratio and cooling capacity. Furthermore, by avoiding the skipping and abnormal wear of the vane 1, the service life of the vane 1 and roller 5 is significantly extended. In traditional structures, the skipping of the vane 1 causes abnormal wear on the head, reducing operational reliability; however, in this solution, the stable contact between the vane 1 and roller 5 reduces wear, lowers maintenance costs, and extends the overall service life of the compressor.

[0049] In one embodiment, such as Figure 3 As shown, the transmission lever 2 includes a first contact portion 22, a second contact portion 23, and a lever shaft 21. The lever shaft 21 is located between the first contact portion 22 and the second contact portion 23, and serves as a support and rotation fulcrum. The first contact portion 22 and the second contact portion 23 face the adjacent first slide plate 1 and the second slide plate 1, respectively, and are in close contact with the tails 11 of the two slide plates. Specifically, the first contact portion 22 contacts the tail 11 of the upper slide plate, and the second contact portion 23 contacts the tail 11 of the lower slide plate. This contact method allows power to be transmitted through the contact between the tail 11 of the slide plate and the transmission lever 2 when one of the slide plates 1 moves.

[0050] Taking a two-cylinder compressor as an example, when the crankshaft 4 drives the roller 5 to move inside the cylinder, the roller 5 pushes the sliding vane 1 that it abuts against to move. Assuming that the upper sliding vane 1 moves outward under the pushing action of the roller 5, the tail 11 of the sliding vane will apply an outward thrust to the first contact part 22 of the transmission lever 2. Due to the supporting effect of the lever shaft 21, the transmission lever 2 rotates around the lever shaft 21. At this time, the second contact part 23 will push the lower sliding vane 1 inward, causing the sliding vane 1 to slide inward, so that the two adjacent sliding vanes 1 move in opposite directions. During the entire transmission process, the lever shaft 21 remains relatively fixed, while the first contact part 22 and the second contact part 23 swing accordingly with the movement of the sliding vane 1, continuously transmitting the motion power of one sliding vane 1 to the other sliding vane 1, ensuring that the two sliding vanes 1 always remain in contact with the roller 5.

[0051] By using lever shaft 21 as a fulcrum for power transmission, the movement direction of adjacent sliding vanes 1 can be precisely controlled. Compared with traditional transmission methods, this structure can avoid the problem of sliding vane 1 disengaging from roller 5 due to inaccurate power transmission. Under various operating conditions of the compressor, it can ensure that sliding vane 1 and roller 5 always maintain close contact, effectively preventing sliding vane 1 from jumping and improving the stability of compressor operation.

[0052] In one embodiment, such as Figure 1 As shown, the sliding plate transmission mechanism also includes a partition plate 3, which is located between two adjacent sliding plates 1. The transmission lever 2 is located on the partition plate 3, and the partition plate 3 has a lever mounting groove 31. The transmission lever 2 is rotatably mounted in the lever mounting groove 31.

[0053] Specifically, taking a two-cylinder compressor as an example, the partition 3 is a flat plate structure, horizontally positioned between the upper and lower cylinders. Corresponding to the vane slot of each cylinder, the partition 3 has a lever slot for mounting the transmission lever 2. The opening direction of the lever slot is parallel to the vane slot, and the width of the lever slot must be greater than the width of the transmission lever 2 so that the transmission lever 2 can be placed inside the lever slot. The lever shaft 21 is installed in the shaft hole 32 on the partition 3, allowing the transmission lever 2 to rotate flexibly around the lever shaft 21. The contact positions of the first contact portion 22 and the second contact portion 23 of the transmission lever 2 with the tail portions 11 of the upper and lower vanes are as follows... Figure 1As shown, when the upper slide plate 1 moves under the push of the roller 5, its tail end transmits power to the transmission lever 2 through contact with the first contact part 22. The transmission lever 2 rotates around the lever shaft 21 as the fulcrum, and then pushes the lower slide plate 1 to move in the opposite direction through the second contact part 23. Throughout the process, the partition 3 remains stable, ensuring the accuracy and reliability of power transmission. Compared with the structure without the support of the partition 3, the presence of the partition 3 allows the transmission lever 2 to more accurately transmit the motion power of one slide plate 1 to another, avoiding the problem of slide plate 1 jumping and power transmission failure caused by the instability of the transmission lever 2, and improving the stability and reliability of the compressor operation.

[0054] In one embodiment, such as Figure 6 As shown, the crankshaft 4 includes a rotating shaft 41 and at least two eccentric portions 42 disposed on the outer periphery of the rotating shaft 41. The number of eccentric portions 42 is the same as that of the rollers 5. All eccentric portions 42 have the same eccentricity, and adjacent eccentric portions 42 are distributed on opposite sides of the crankshaft 4. The eccentric portions 42 abut against the inner surface of the rollers 5.

[0055] When the compressor starts, the motor drives the crankshaft 44's shaft 41 to rotate. Due to the eccentric design of the eccentric part 42 and the shaft 41, the eccentric part 42 will rotate around the central axis of the shaft 41 during rotation. This movement of the eccentric part 42 will push the roller 5 it contacts to rotate within the cylinder. Taking a two-cylinder compressor as an example, when one eccentric part 42 pushes the roller 5 in the corresponding cylinder in a certain direction, the other eccentric part 42 located on the opposite side of the shaft 41 will push its corresponding roller 5 in the opposite direction, thus realizing the alternating operation of the two cylinders. Throughout the entire operation, since the eccentricity of all eccentric parts 42 is the same, the consistency and stability of the movement of the roller 5 in each cylinder are ensured, enabling the compressor to operate efficiently and smoothly.

[0056] Furthermore, the length of the transmission lever 2 must satisfy: L > H / sin(α), where α is the angle between the direction of the working limit position of the transmission lever 2 and the horizontal direction, H is the vertical height from the position of the lever shaft 21 to the contact position between the transmission lever 2 and the slider 1, and L is the length of the transmission lever 2. By reasonably designing the length of the transmission lever 2, it can be ensured that the transmission lever 2 effectively transmits power during the movement of the slider 1, avoiding the phenomenon of the slider 1 disengaging from the roller 5 due to improper length of the transmission lever 2.

[0057] It should be noted that by changing the contact position between the tail 11 of the slider and the transmission lever 2, the changing speed of the slider 1 throughout the complete cycle can be accommodated. For example... Figure 9As shown, O0 is the rotation center of crankshaft 4, O1 is the rotation center of roller 4, and O2 is the head center of vane 1. Calculations show that the position of vane 1 is related to the eccentricity of crankshaft 4, the radius of roller 5, and the angle between the line connecting the rotation center of crankshaft 4 and the center of eccentric part 42 and the vane groove (which can be represented by the initial position of compressor eccentric part 42, rotational speed, and time). The relationship is shown in the following equation: In the formula: L θ Let θ be the position of the slider 1 from the rotation center of the crankshaft 4, θ be the angle between the line connecting the rotation center of the crankshaft 4 and the center of the eccentric part 42 and the slider groove, e be the eccentricity of the eccentric part 42, and R be the radius of the roller 5. θ Taking the derivative with respect to θ, we can calculate the rate of change of position of slider 1 with respect to the rotation angle: It can be seen that the rate of change of the position of slide vane 1 changes with the rotation of crankshaft 4 driven by the compressor motor. As the angle between the line connecting the rotation center of crankshaft 4 and the center of eccentric part 42 and the slide vane groove increases, the absolute value of the rate of change of the position of slide vane 1 with the angle shows a trend of first increasing and then decreasing. Observing with the specific value R = 2e, it is found that the maximum absolute value of the rate of change occurs approximately when the rotation angle is 67°. The rate of change of the position of slide vane 1 with the angle is less than zero, indicating that from the point where the line connecting the rotation center of crankshaft 4 and the center of eccentric part 42 coincides with the slide vane groove until crankshaft 4 rotates 180°, the distance between slide vane 1 and the rotation center gradually decreases from the maximum value R + e to the minimum value Re, and the decrease becomes faster and faster. If crankshaft 4 continues to rotate to 360°, it will be found that slide vane 1 gradually moves away from the rotation center, and the speed of moving away gradually accelerates. Therefore, based on the calculated relationship between the position of slide vane 1 and the rotation angle of crankshaft 4, the shape of the tail 11 of slide vane can be optimized. Generally, the shape of the position where the tail 11 of the slider contacts the transmission lever 2 is designed to be an arc shape or a sharp corner shape.

[0058] In one embodiment, the transmission lever 2 is made of an elastic material, specifically spring steel, beryllium bronze, or other elastic metal materials. This design avoids the possibility of the sliding vane 1 disengaging from the roller 5 that might occur with rigid transmission, significantly reducing the probability of leakage and improving the compressor's sealing performance.

[0059] like Figure 8 As shown, this embodiment of the invention also provides a compressor, including the pump body assembly described above. Apart from the pump body assembly, the remaining structure of the compressor is the same as that in the prior art, and will not be described in detail here.

[0060] The overall work process is as follows:

[0061] Taking a two-cylinder compressor as an example, when the two-cylinder compressor is powered on and started, the motor drives the crankshaft 4 to start rotating. As the crankshaft 4 rotates, the eccentric part 42 makes a circular motion around the central axis of the rotating shaft 41, which in turn pushes the two rollers 5 to make a circular motion in the working chamber of their respective cylinders.

[0062] Inside the upper cylinder, the roller 5 moves in a certain direction under the push of the eccentric part 42. The movement of the roller 5 compresses the refrigerant gas in the working chamber, increasing the pressure in that area, and simultaneously pushing the upper slide plate 1, which abuts against the outer surface of the roller 5, to slide in the slide plate groove. The tail 11 of the upper slide plate contacts the first contact part 22 of the transmission lever 2, and when the upper slide plate 1 slides, it applies a pushing force to the first contact part 22.

[0063] After being pushed by the upper sliding plate 1, the transmission lever 2 transmits power using the lever principle. The transmission lever 2 rotates around the lever shaft 21 as the fulcrum, pushing the lower sliding plate 1 in the cylinder to slide in the opposite direction through the second contact part 23.

[0064] Inside the lower cylinder, the lower sliding vane 1, pushed by the transmission lever 2, drives the roller 5 to move in the opposite direction. At this time, the working chamber volume of the lower cylinder changes, performing operations such as intake and compression of the refrigerant gas. Throughout the process, the upper and lower cylinders alternately perform intake, compression, and exhaust operations. Figure 8 As shown, Figure 8 The movement of transmission lever 2 during compressor operation is shown.

[0065] During compressor operation, as the crankshaft 4 continuously rotates, the rollers 5 and vanes 1 reciprocate continuously. Due to the action of the transmission lever 2, adjacent vanes 1 always move in opposite directions, and the head of the vane 1 remains in contact with the outer surface of the roller 5, preventing vane 1 from jumping. Simultaneously, the elastic deformation characteristics of the transmission lever 2 effectively absorb and buffer the impact and vibration during operation, reducing wear and noise between components, improving the stability and reliability of compressor operation, reducing the possibility of refrigerant leakage, and increasing the compressor's energy efficiency ratio.

[0066] The above description is merely a specific embodiment of the present invention, but the scope of protection of the present invention is not limited thereto. Any person skilled in the art can easily conceive of various equivalent modifications or substitutions within the technical scope disclosed in the present invention, and these modifications or substitutions should all be covered within the scope of protection of the present invention. Therefore, the scope of protection of the present invention should be determined by the scope of the claims.

Claims

1. A sliding vane transmission mechanism, characterized in that, include: At least two sliders are arranged vertically on adjacent sliders; The transmission lever contacts the tail ends of the two adjacent sliding plates; When one of the two adjacent sliders is subjected to force and moves, the transmission lever drives the other slider to move, and the two adjacent sliders move in opposite directions; The transmission lever includes a first contact portion, a second contact portion, and a lever shaft, the lever shaft being disposed between the first contact portion and the second contact portion, and the first contact portion and the second contact portion respectively contacting two adjacent sliding pieces; the length of the transmission lever satisfies: ,in, The angle between the working limit position direction of the transmission lever and the horizontal direction. The vertical height from the position of the lever shaft to the contact position between the transmission lever and the slider. The length of the transmission lever.

2. The sliding vane transmission mechanism according to claim 1, characterized in that, The transmission lever is made of elastic material.

3. A sliding vane transmission mechanism according to any one of claims 1-2, characterized in that, It also includes a partition plate, which is disposed between two adjacent sliding plates, and the transmission lever is disposed on the partition plate.

4. A sliding vane transmission mechanism according to claim 3, characterized in that, The partition plate has a lever mounting groove, and the transmission lever is rotatably mounted in the lever mounting groove.

5. A sliding vane transmission mechanism according to claim 4, characterized in that, The position where the tail of the slider contacts the transmission lever is either arc-shaped or sharp-angled.

6. A pump body assembly, characterized in that, The invention includes a sliding vane transmission mechanism, a crankshaft, at least two cylinders, and at least two rollers as described in any one of claims 1-5. Each cylinder is provided with a working chamber and a sliding vane groove. The crankshaft passes through the working chamber, and the roller is sleeved on the crankshaft and located in the working chamber. The sliding vane is slidably disposed in the sliding vane groove, and the head of the sliding vane abuts against the outer surface of the roller.

7. A pump body assembly according to claim 6, characterized in that, The crankshaft includes a shaft and at least two eccentric portions disposed on the outer periphery of the shaft. All the eccentric portions have the same eccentricity, and adjacent eccentric portions are distributed on opposite sides of the crankshaft. The eccentric portions abut against the inner surface of the roller.

8. A compressor, characterized in that, Includes the pump body assembly as described in any one of claims 6-7.

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