Sliding vane transmission mechanism, pump body assembly and compressor

Abstract

The invention discloses a sliding vane transmission mechanism, a pump body assembly and a compressor. The sliding vane transmission mechanism comprises at least two sliding vanes, and every two adjacent sliding vanes are arranged up and down; the transmission lever is in contact with the tail parts of the two adjacent sliding sheets; when one of the two adjacent sliding sheets is stressed to move, the transmission lever drives the other sliding sheet to move, and the two adjacent sliding sheets move in opposite directions. Driving force needed by movement of the sliding piece is transmitted according to the lever principle, it is ensured that the sliding piece and the roller are in an abutting state all the time, and compared with time delay and hysteresis problems existing in a traditional spring structure, the response speed is higher, so that it is ensured that the sliding piece and the roller are tightly attached all the time, and the problem that the sliding piece jumps in the running process is solved.

Description

Technical Field

[0001] The present invention relates to the technical field of compressors, and in particular to a vane transmission mechanism, a pump assembly and a compressor. Background Art

[0002] As a core component of refrigeration and air conditioning, the performance of the compressor directly impacts the cooling capacity, energy efficiency, and noise level of the air conditioner. With improvements in living standards, high efficiency and low noise levels in air conditioning compressors are key trends in the industry. Vanes are a significant source of frictional power loss and mechanical noise. Currently, in rotary compressors for air conditioners, the vanes maintain contact between the head and rollers through the force of a spring at the tail and the unbalanced gas force between the head and tail.

[0003] The use of spring force and unbalanced gas force to keep the vane's head in constant contact with the roller presents the following problems: The vane is prone to vibrating and separating from the roller during the initial startup of the compressor, the final exhaust phase, or high-frequency operation. In the initial stages of operation, the pressure differential between the suction and exhaust chambers has not yet been established, and the vane may vibrate due to insufficient pressure differential between the head and tail, causing abnormal wear on the head. At the final exhaust phase, the exhaust pressure in the cylinder rises sharply, reducing the pressure differential across the vane, potentially preventing the vane from fitting tightly against the roller surface. At high-frequency operation, the vane's reciprocating speed in the vane slot increases, requiring a larger pressure differential. If the actual pressure differential is insufficient, this can also cause the vane to vibrate.

[0004] When the vanes bounce, they repeatedly cycle between the vanes and rollers in contact, disengagement, and re-contact, causing collisions between moving parts and generating loud operating noise. Furthermore, vane bounce causes abnormal wear on the head, reducing operational reliability. Disengagement between the vanes and rollers can also cause refrigerant leaks, reducing overall unit performance. Summary of the Invention

[0005] The purpose of the present invention is to overcome the deficiencies of the prior art and to provide a vane transmission mechanism, a pump assembly and a compressor, in order to solve the problem of vane jumping during the operation of the compressor.

[0006] To achieve the above object, the present invention adopts the following technical solutions:

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

[0008] At least two slides, two adjacent slides are arranged one above the other;

[0009] a transmission lever in contact with the tails of two adjacent slides;

[0010] When one of the two adjacent sliding plates moves under force, the transmission lever drives the other sliding plate to move, and the movement directions of the two adjacent sliding plates are opposite.

[0011] Furthermore, the transmission lever includes a first contact portion, a second contact portion and a lever shaft, the lever shaft is provided between the first contact portion and the second contact portion, and the first contact portion and the second contact portion are in contact with two adjacent sliding sheets respectively.

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

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

[0014] Furthermore, it also includes a partition, which is arranged between two adjacent slides, and the transmission lever is arranged on the partition.

[0015] Furthermore, the partition is provided with a lever installation groove, and the transmission lever is rotatably arranged in the lever installation groove.

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

[0017] In the second aspect, the present invention also provides a pump body assembly, including the above-mentioned vane transmission mechanism, a crankshaft, at least two cylinders and at least two rollers, each of the cylinders is provided with a working chamber and a vane groove, the crankshaft is passed through the working chamber, the roller is sleeved on the crankshaft and located in the working chamber, the vane is slidably arranged in the vane groove, and the head of the vane abuts against the outer surface of the roller.

[0018] Furthermore, the crankshaft includes a rotating shaft and at least two eccentric parts arranged on the outer peripheral side of the rotating shaft. The eccentricity of all the eccentric parts is the same, and adjacent eccentric parts are distributed on opposite sides of the crankshaft. The eccentric parts abut against the inner surface of the roller.

[0019] In a third aspect, the present invention further provides a compressor comprising the above-mentioned pump body assembly.

[0020] Compared with the prior art, the present invention has the following advantages: a slide transmission mechanism includes at least two slides, with two adjacent slides arranged one above the other; a transmission lever in contact with the tails of the two adjacent slides; when one of the two adjacent slides is forced to move, the transmission lever drives the other slide to move, and the two adjacent slides move in opposite directions. The present invention utilizes the principle of leverage to transmit the driving force required for the slide movement, ensuring that the slide and roller are always in contact. Compared with the delay and hysteresis problems of traditional spring structures, the response speed is faster, thereby ensuring that the slide and roller are always in close contact, and avoiding the problem of slide jumping during operation.

[0021] The above description is only an overview of the technical solution of the present invention. In order to more clearly understand the technical means of the present invention, it can be implemented in accordance with the contents of the specification. In order to make the above and other purposes, features and advantages of the present invention more obvious and easy to understand, the following preferred embodiments are specifically cited and described in detail as follows. BRIEF DESCRIPTION OF THE DRAWINGS

[0022] In order to more clearly illustrate the technical solutions of the embodiments of the present invention, the following briefly introduces the drawings required for use in the description of the embodiments. Obviously, the drawings described below are some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying any creative work.

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

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

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

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

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

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

[0029] Figure 7 A motion diagram of a transmission lever according to a specific embodiment of the present invention;

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

[0031] Figure 9 Schematic diagram of the relationship between the various components of the compressor.

[0032] Reference numerals

[0033] 1. Slide; 11. Tail of slide; 12. Head of slide; 2. Transmission lever; 21. Lever shaft; 22. First contact portion; 23. Second contact portion; 3. Partition; 31. Lever mounting groove; 32. Shaft hole; 4. Crankshaft; 41. Rotating shaft; 42. Eccentric portion; 5. Roller. DETAILED DESCRIPTION

[0034] The following will clearly and completely describe the technical solutions of the present invention in conjunction with specific embodiments of the present invention. Obviously, the embodiments described are only part of the embodiments of the present invention, not all of them. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without making creative efforts are within the scope of protection of the present invention.

[0035] In the description of the present invention, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", "clockwise", "counterclockwise", "axial", "radial", "circumferential" and the like to indicate orientations or positional relationships based on the orientations or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be understood as limiting the present 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 the technical features being referred to. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one such feature. In the description of the present invention, "plurality" means at least two, such as two, three, etc., unless otherwise specifically defined.

[0037] In the present invention, unless otherwise specified or limited, the terms "installed," "connected," "connect," "fixed," etc. should be understood in a broad sense. For example, they can refer to fixed connection, detachable connection, or integration; mechanical connection, electrical connection; direct connection, or indirect connection through an intermediate medium; internal communication between two components, or interaction between two components, unless otherwise specified. Those skilled in the art will understand the specific meanings of the above terms in the present invention based on specific circumstances.

[0038] In the present invention, unless otherwise expressly specified or limited, when a first feature is "above" or "below" a second feature, it may mean that the first and second features are in direct contact, or that the first and second features are in indirect contact through an intermediary. Furthermore, when a first feature is "above," "above," or "above" a second feature, it may mean that the first feature is directly above or diagonally above the second feature, or simply means that the first feature is at a higher level than the second feature. When a first feature is "below," "below," or "below" a second feature, it may mean that the first feature is directly below or diagonally below the second feature, or simply means that the first feature is at a lower level than the second feature.

[0039] It should be noted that when an element is referred to as being "fixed to" or "disposed on" another element, it may be directly on the other element or there may be an intermediate element. When an element is considered to be "connected to" another element, it may be directly connected to the other element or there may be an intermediate 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 implementation methods.

[0040] As a core component of refrigeration and air conditioning, the performance of the compressor directly impacts the cooling capacity, energy efficiency, and noise level of the air conditioner. With improvements in living standards, high efficiency and low noise levels in air conditioning compressors are becoming key trends in the industry. The vane 1 is a significant source of frictional power loss and mechanical noise. In current rotary compressors for air conditioners, the vane 1 maintains constant contact between the head 12 and the roller 5, driven by a spring force at the tail and the unbalanced gas force between the head and tail.

[0041] The spring force and unbalanced gas force force the vane's head 12 to maintain constant contact with the roller 5. This presents the following problems: During the initial startup of the compressor, the final exhaust phase, or high-frequency operation, the vane 1 is prone to bouncing, causing separation between the vane 1 and the roller 5. In the initial stages of operation, the pressure differential between the suction and exhaust chambers has not yet been established, and the vane 1 may bob due to insufficient pressure differential between the head and tail, causing abnormal wear on the head. At the final exhaust phase, the exhaust pressure in the cylinder rises sharply, reducing the pressure differential across the vane 1, potentially preventing the vane 1 from fitting tightly against the surface of the roller 5. Under high-frequency operation, the reciprocating speed of the vane 1 in the vane slot increases, increasing the required pressure differential. If the actual pressure differential is insufficient, this will also cause the vane 1 to bob.

[0042] When the vane 1 bounces, it repeatedly cycles between contact, disengagement, and contact with the roller 5, causing collisions between moving parts and generating loud operating noise. Furthermore, the bounce of the vane 1 causes abnormal wear on the head, reducing operational reliability. Disengagement between the vane 1 and the roller 5 can also cause refrigerant leakage, reducing overall machine performance. In light of these circumstances, the present invention has been proposed and will be described below through specific embodiments.

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

[0044] like Figures 1 to 9 As shown, an embodiment of the present 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 is passed through the working chamber, the roller 5 is sleeved on the crankshaft 4 and is 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 tail 11 of the 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, and the movement directions of the two adjacent vanes 1 are opposite, the two adjacent vanes 1 are arranged up and down, the vane 1 is slidably arranged in the vane groove, and the head 12 of the vane abuts the outer surface of the roller 5.

[0045] Specifically, a two-cylinder compressor consists of two cylinders, each with an independent working chamber and vane slot. The working chamber provides space for the movement of roller 5 and crankshaft 4, while the vane slot accommodates vane 1 and restricts its motion. Crankshaft 4 runs through the working chambers of both cylinders. Roller 5 is sleeved on crankshaft 4 and located within the working chamber, allowing it to perform circular motion driven by crankshaft 4.

[0046] Two slides 1 slide in the slide slots of the two cylinders, respectively. The number of slides 1 corresponds to the number of cylinders, and two adjacent slides 1 are arranged one above the other. The head 12 of the slide can tightly abut the outer surface of the roller 5; the tail 11 of the slide is used to contact the transmission lever 2.

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

[0048] Connecting adjacent vanes 1 through a lever transmission ensures consistent movement of the vanes 1, effectively overcoming the problem of vane 1 bouncing in conventional structures caused by insufficient pressure differentials and excessive frequency. In conventional structures, vanes 1 are prone to disengagement from roller 5 during the initial startup phase, the final exhaust phase, or high-frequency operation of the compressor. In this solution, the transmission lever 2 promptly transmits power, ensuring that the vanes 1 always maintain contact with the roller 5, avoiding collisions between moving parts caused by vane 1 bouncing. This significantly reduces operating noise and improves the stability and reliability of the compressor. Furthermore, the lever transmission structure prevents disengagement between the vanes 1 and the roller 5, reducing the possibility of refrigerant leakage. Conventional spring structures suffer from delays and hysteresis, making it impossible to ensure a close fit between the vanes 1 and the roller 5 under certain operating conditions, leading to refrigerant leakage and reduced overall performance. The lever transmission of the present invention, however, offers a fast response speed and ensures a close fit between the vanes 1 and the roller 5, effectively preventing refrigerant leakage and improving the compressor's energy efficiency and cooling capacity. Furthermore, by eliminating vane 1 vibration and abnormal wear, the service life of vane 1 and roller 5 is significantly extended. In conventional designs, vane 1 vibration can cause abnormal wear on the head, reducing operational reliability. In this solution, however, the stable contact between vane 1 and roller 5 reduces wear, lowers maintenance costs, and extends the overall service life of the compressor.

[0049] In one embodiment, if 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 disposed between the first contact portion 22 and the second contact portion 23. The lever shaft 21 serves as a support and rotation fulcrum. The first contact portion 22 and the second contact portion 23 face the adjacent first and second slides 1, respectively, and are in close contact with the tails 11 of the two slides. Specifically, the first contact portion 22 contacts the tail 11 of the upper slide, and the second contact portion 23 contacts the tail 11 of the lower slide. This contact method enables power to be transmitted through the contact between the tail 11 of the slide and the transmission lever 2 when one of the slides 1 moves.

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

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

[0052] In one embodiment, if Figure 1 As shown, the slide transmission mechanism also includes a partition 3, which is arranged between two adjacent slides 1, and a transmission lever 2 is arranged on the partition 3. The partition 3 is provided with a lever mounting groove 31, and the transmission lever 2 is rotatably arranged in the lever mounting groove 31.

[0053] Specifically, taking a two-cylinder compressor as an example, the partition 3 is a flat plate structure, which is horizontally arranged between the upper and lower cylinders. The partition 3 corresponds to the position of the slide groove of each cylinder, and is provided with a lever groove for installing the transmission lever 2. The opening direction of the lever groove is parallel to the slide groove. The width of the lever groove must be greater than the width of the transmission lever 2 so that the transmission lever 2 can be placed in the lever groove. The lever shaft 21 is installed in the shaft hole 32 on the partition 3, so that the transmission lever 2 can rotate flexibly around the lever shaft 21. The contact position of the first contact portion 22 and the second contact portion 23 of the transmission lever 2 with the tail 11 of the upper and lower slides is as shown in FIG. Figure 1As shown. When the upper vane 1 moves under the push of the roller 5, its tail contacts the first contact portion 22 of the transmission lever 2, transmitting power to the transmission lever 2. The transmission lever 2 rotates with the lever shaft 21 as the fulcrum, and then pushes the lower vane 1 in the opposite direction through the second contact portion 23. During the entire process, the partition 3 remains stable, ensuring the accuracy and reliability of power transmission. Compared to a structure without the support of the partition 3, the presence of the partition 3 enables the transmission lever 2 to more accurately transmit the motion power of one vane 1 to another vane 1, avoiding the problem of vane 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, if Figure 6 As shown, the crankshaft 4 includes a rotating shaft 41 and at least two eccentric portions 42 arranged on the outer peripheral side of the rotating shaft 41. The number of the eccentric portions 42 is the same as the number of the rollers 5. The eccentricity of all the eccentric portions 42 is the same, 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 is started, the motor drives the rotating shaft 41 of the crankshaft 4 to rotate. Due to the eccentric design of the eccentric part 42 and the rotating shaft 41, during the rotation of the rotating shaft 41, the eccentric part 42 will make a circular motion around the central axis of the rotating shaft 41. This movement of the eccentric part 42 will push the roller 5 in contact with it to make a circular motion in the cylinder. Taking a two-cylinder compressor as an example, when one eccentric part 42 pushes the roller 5 in the corresponding cylinder to move in a certain direction, the other eccentric part 42 on the opposite side of the rotating shaft 41 will push its corresponding roller 5 to move in the opposite direction, thereby realizing the alternating operation of the two cylinders. During the entire working process, 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 is guaranteed, so that the compressor can operate efficiently and smoothly.

[0056] Furthermore, the length of the transmission lever 2 must satisfy the following relationship: L > H / sin(α), where α is the angle between the transmission lever 2's operating limit position and the horizontal, H is the vertical height from the lever shaft 21 to the contact point between the transmission lever 2 and the slide 1, and L is the length of the transmission lever 2. By properly designing the length of the transmission lever 2, it is possible to ensure that the transmission lever 2 always effectively transmits power during the movement of the slide 1, preventing the slide 1 from separating from the roller 5 due to an inappropriate length of the transmission lever 2.

[0057] It should be noted that by changing the contact position between the tail 11 of the slide and the transmission lever 2, it is possible to adapt to the change in the moving speed of the slide 1 in a complete cycle. Figure 9As shown, O0 is the rotation center of the crankshaft 4, O1 is the rotation center of the roller 4, and O2 is the center of the head of the vane 1. Calculations show that the position of the vane 1 is related to the eccentricity of the crankshaft 4, the radius of the roller 5, and the angle between the line connecting the rotation center of the crankshaft 4 and the center of the eccentric portion 42 and the vane slot (which can be expressed as the initial position of the compressor eccentric portion 42, the rotation speed, and time). The relationship is shown in the formula: Where: L θ is the position of the vane 1 from the rotation center of the crankshaft 4, θ is the angle between the line connecting the rotation center of the crankshaft 4 and the center of the eccentric part 42 and the vane groove, e is the eccentricity of the eccentric part 42, and R is the radius of the roller 5. θ By taking the derivative of θ, we can calculate the rate of change of the position of the slider 1 with respect to the rotation angle: It can be seen that the rate of change of vane 1's position changes as the compressor motor drives the crankshaft 4. As the angle between the line connecting the center of rotation of the crankshaft 4 and the center of the eccentric portion 42 and the vane slot increases, the absolute value of the rate of change of vane 1's position with angle increases and then decreases. Observing the specific value of R = 2e, the maximum absolute value of the rate of change occurs approximately at a rotation angle of 67°. The rates of change of vane 1's position with angle are all less than zero, indicating that from the point where the line connecting the center of rotation of the crankshaft 4 and the center of the eccentric portion 42 coincides with the vane slot until the crankshaft 4 rotates 180°, the distance between vane 1 and the rotation center gradually decreases from a maximum value of R + e to a minimum value of Re, decreasing at an increasingly rapid rate. As the crankshaft 4 continues to rotate to 360°, vane 1 gradually moves away from the rotation center, and the rate of distance increases. Therefore, the calculated relationship between vane 1's position and the rotation angle of the crankshaft 4 can be used to optimize the shape of the vane's tail 11. Generally, the shape of the position where the tail portion 11 of the slide contacts the transmission lever 2 is designed to be an arc shape or a sharp angle shape.

[0058] In one embodiment, the transmission lever 2 is made of an elastic material, specifically a metal elastic material such as spring steel or beryllium bronze. This design avoids the phenomenon of the slide 1 and the roller 5 being separated due to a rigid transmission, significantly reduces the probability of leakage, and improves the sealing performance of the compressor.

[0059] like Figure 8 As shown, an embodiment of the present invention further provides a compressor, comprising the above-mentioned pump body assembly. Except for the above-mentioned pump body assembly, the rest of the structure of the compressor can be the same as that in the prior art, and the rest of the structure is not repeated here.

[0060] The overall working process is as follows:

[0061] Taking the operation of a two-cylinder compressor as an example, when the two-cylinder compressor is powered on and started, the motor drives the crankshaft 4 to begin rotating. As the crankshaft 4 rotates, the eccentric portion 42 performs a circular motion around the central axis of the rotating shaft 41, thereby driving the two rollers 5 to perform a circular motion in the working chambers of their respective cylinders.

[0062] Inside the upper cylinder, roller 5, propelled by eccentric portion 42, moves in a specific direction. This movement compresses the refrigerant gas within the working chamber, increasing the pressure there. This movement also pushes upper vane 1, which abuts the outer surface of roller 5, to slide within the vane groove. The tail portion 11 of the upper vane contacts the first contact portion 22 of transmission lever 2. As upper vane 1 slides, it applies a thrust to first contact portion 22.

[0063] After receiving the thrust of the upper slide 1, the transmission lever 2 transmits the power by the lever principle. The transmission lever 2 rotates with the lever shaft 21 as the fulcrum, pushing the slide 1 in the cylinder below to slide in the opposite direction through the second contact portion 23.

[0064] In the lower cylinder, the lower slide 1, driven 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, and the refrigerant gas is sucked in and compressed. In the whole process, the upper and lower cylinders alternately perform suction, compression, exhaust and other work processes. Figure 8 As shown, Figure 8 The movement of the transmission lever 2 when the compressor is running is shown.

[0065] During compressor operation, as crankshaft 4 rotates continuously, roller 5 and vane 1 undergo continuous reciprocating motion. Drive lever 2 ensures that adjacent vanes 1 always move in opposite directions, and the heads of vanes 1 maintain contact with the outer surface of roller 5, preventing vane 1 from bouncing. Furthermore, the elastic deformation properties of drive lever 2 effectively absorb and cushion impact forces and vibrations during movement, reducing wear and noise between components, improving compressor operation stability and reliability, and lowering the likelihood of refrigerant leakage, thereby increasing the compressor's energy efficiency.

[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 such modifications or substitutions are intended to be within the scope of protection of the present invention. Therefore, the scope of protection of the present invention shall be subject to the scope of protection of the claims.

Claims

1. A sliding vane transmission mechanism, characterized in that: include: At least two slides, two adjacent slides are arranged one above the other; a transmission lever in contact with the tails of two adjacent slides; When one of the two adjacent sliding plates moves under force, the transmission lever drives the other sliding plate to move, and the movement directions of the two adjacent sliding plates are opposite.

2. A sliding vane transmission mechanism according to claim 1, characterized in that: The transmission lever includes a first contact portion, a second contact portion, and a lever shaft. The lever shaft is disposed between the first contact portion and the second contact portion. The first contact portion and the second contact portion are in contact with two adjacent sliding sheets, respectively.

3. A sliding vane transmission mechanism according to claim 2, characterized in that: The length of the transmission lever satisfies: L>H / sin(α), where α is the angle between the working limit position direction of the transmission lever and the horizontal direction, H is the vertical height from the position of the lever axis to the contact position between the transmission lever and the slide, and L is the length of the transmission lever.

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

5. A sliding vane transmission mechanism according to any one of claims 1 to 4, characterized in that: It also includes a partition plate, which is arranged between two adjacent slides, and the transmission lever is arranged on the partition plate.

6. The sliding vane transmission mechanism according to claim 5, characterized in that: The partition is provided with a lever installation slot, and the transmission lever is rotatably arranged in the lever installation slot.

7. The sliding vane transmission mechanism according to claim 6, characterized in that: The position where the tail of the slide contacts the transmission lever is in an arc shape or a sharp angle shape.

8. A pump assembly, characterized in that: It comprises the vane transmission mechanism according to any one of claims 1 to 7, a crankshaft, at least two cylinders and at least two rollers, each of the cylinders is provided with a working chamber and a vane groove, the crankshaft is passed through the working chamber, the roller is sleeved on the crankshaft and is located in the working chamber, the vane is slidably arranged in the vane groove, and the head of the vane abuts against the outer surface of the roller.

9. A pump assembly according to claim 8, characterized in that: The crankshaft includes a rotating shaft and at least two eccentric parts arranged on the outer peripheral side of the rotating shaft. The eccentricity of all the eccentric parts is the same, and adjacent eccentric parts are distributed on opposite sides of the crankshaft. The eccentric parts abut against the inner surface of the roller.

10. A compressor, characterized in that: The pump body assembly comprises the pump body assembly according to any one of claims 8 to 9.

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