Compression mechanism

Abstract

A compression mechanism comprises a first compression body, a second compression body and a rotatable cam. The first compression body comprises a first piston; the first piston comprises a first piston rod and a first piston head; the second compression body comprises a second piston which is provided with a second piston rod and a second piston head. The cam is configured to rotate along a rotating shaft under the condition of being driven; the rotating shaft is perpendicular to the plane where the cam is located. One end of the first piston rod away from the first piston head and one end of the second piston rod away from the second piston head abut against the rim of the cam. The axial direction of the first piston rod and the axial direction of the second piston rod are collinear and parallel to the plane where the cam is located. The wheel flange is provided with at least two abutting points with unequal radiuses of rotation tracks; wherein different abutting points are different in the radial direction of the cam. According to the compression mechanism, the two pistons are collinearly arranged, inertia moment generated by reciprocating motion of the pistons is counteracted to a certain extent, and the stability and reliability of the compression mechanism are improved.

Description

Technical Field

[0001] The present application relates to the technical field of compressors, and more particularly, to a compression mechanism. Background Art

[0002] A compression mechanism is generally a mechanism for compressing substances. Commonly used compression mechanisms usually have a reciprocating structure. Such compression mechanisms usually have two compression bodies that are centrosymmetric.

[0003] In a reciprocating compression mechanism, the movement directions of the pistons in the two compression bodies are usually opposite. Moreover, the pistons in the two compression bodies usually move synchronously. That is to say, the two pistons usually move in opposite directions synchronously.

[0004] However, even if the two pistons move in opposite directions synchronously, the inertial torque caused by the pistons during their movement on the entire compression mechanism can still have a significant impact on the stability and reliability of the compression mechanism. Summary of the Invention

[0005] The purpose of the present application is to provide a compression mechanism in which the pistons in the two compression bodies are arranged collinearly, thereby being able to offset to a certain extent the inertial torque generated by the reciprocating movement of the pistons on the compression mechanism, and ultimately improving the stability and reliability of the compression mechanism.

[0006] The compression mechanism provided by the present application includes a first compression body, a second compression body and a rotatable cam; the first compression body includes a first piston, and the first piston includes a first piston rod and a first piston head; the second compression body includes a second piston, and the second piston has a second piston rod and a second piston head; the cam is configured to rotate along a rotation axis when being driven; wherein, the rotation axis is perpendicular to the plane where the cam is located; one end of the first piston rod away from the first piston head and one end of the second piston rod away from the second piston head respectively abut against the rim of the cam; the axial direction of the first piston rod and the axial direction of the second piston rod are collinear and parallel to the plane where the cam is located; there are at least two abutting points on the rim with unequal radii of the rotation trajectories; wherein, different said abutting points are different in the radial direction of the cam.

[0007] The above compression mechanism drives the reciprocating motion of the first piston and the second piston because the rim of the cam has at least two abutting points with unequal radii and different radial positions in the rotational trajectories. On this basis, through the design that the axial direction of the first piston rod is collinear with the axial direction of the second piston rod, the inertial torques brought by the two to the entire compression mechanism are offset to a certain extent. That is, because the moving directions of the first piston and the second piston are opposite and collinear, there is usually no inertial torque between the inertial forces they bring to the entire compression mechanism. Furthermore, the stability and reliability of the compression mechanism are improved.

[0008] Optionally, the cam includes an elliptical wheel.

[0009] For the above compression mechanism, when using an elliptical wheel as the cam, there is no need to consider whether the position of the rotation axis is eccentrically set as when selecting a circular wheel as the cam, thus realizing the drive of the reciprocating motion of the first piston and the second piston. That is to say, using an elliptical wheel as the cam makes the selection of the rotation axis position more flexible.

[0010] Optionally, the rotation axis of the elliptical wheel passes through the center of the elliptical wheel.

[0011] For the above compression mechanism, by selecting an elliptical wheel as the cam and the rotation axis can pass through the center of the elliptical wheel, the first piston and the second piston can perform reciprocating motion synchronously. Furthermore, the inertial torques brought by the reciprocating motion of the first piston and the second piston to the entire compression mechanism are almost completely offset. Finally, the stability and reliability of the compression mechanism are further improved.

[0012] Optionally, one end of the first piston rod away from the first piston head has a first arc-shaped end face; the first arc-shaped end face bends towards the first piston head, and the bending direction is parallel to the plane where the cam is located; the first arc-shaped end face abuts against the rim of the cam; and / or one end of the second piston rod away from the second piston head has a second arc-shaped end face; the second arc-shaped end face bends towards the second piston head, and the bending direction is parallel to the plane where the cam is located; the second arc-shaped end face abuts against the rim of the cam.

[0013] For the above compression mechanism, when one end of the first piston rod away from the first piston head and one end of the second piston rod away from the second piston head respectively abut against the rim of the cam, relative sliding will occur between the rim of the cam and one end of the first piston rod away from the first piston head and one end of the second piston rod away from the second piston head during the rotation of the cam.

[0014] Optionally, the first piston head is detachably connected to the first piston rod; and / or the second piston head is detachably connected to the second piston rod.

[0015] The above compression mechanism, by detachably connecting the first piston head to the first piston rod and / or the second piston head to the second piston rod, enables the first piston head, the first piston rod, and / or the second piston head and the second piston rod to be replaced without replacing the first piston and / or the second piston as a whole in case of failure. Thus, the maintenance cost of the compression mechanism is reduced.

[0016] Optionally, the first piston head has a first piston head flange facing the first piston rod; one end of the first piston rod facing the first piston head has a first piston rod flange; the first piston head flange and the first piston rod flange are connected by a first fastener; and / or the second piston head has a second piston head flange facing the second piston rod; one end of the second piston rod facing the second piston head has a second piston rod flange; the second piston head flange and the second piston rod flange are connected by a second fastener.

[0017] In the above compression mechanism, the first piston head and the first piston rod are connected by a flange, and / or the second piston head and the second piston rod are connected by a flange, which improves the disassembly convenience and installation stability between the first piston head and the first piston rod, and / or between the second piston head and the second piston rod.

[0018] Optionally, the first compression body is provided with a first clamping member; the first clamping member clamps the first piston rod and is configured to limit the movement direction of the first piston rod to the axial direction of the first piston rod; and / or the second compression body is provided with a second clamping member; the second clamping member clamps the second piston rod and is configured to limit the movement direction of the second piston rod to the axial direction of the second piston rod.

[0019] In the above compression mechanism, by clamping the first piston rod by the first clamping member and / or clamping the second piston rod by the second clamping member, the swing of the first piston rod and / or the second piston rod is limited to a certain extent, thereby further improving the stability and reliability of the compression mechanism.

[0020] Optionally, the compression mechanism further includes a drive shaft; the cam includes a cam body and an anti-slip member;

[0021] A through hole is provided on the cam body; the drive shaft passes through the through hole, one end of the anti-slip member is connected to the hole wall of the through hole, and the other end is connected to the drive shaft; the axial direction of the drive shaft is parallel to the rotation axis and is configured to drive the cam to rotate when it rotates.

[0022] In the above compression mechanism, by providing an anti-slip member between the cam and the drive shaft, the slipping between the cam and the drive shaft is prevented to a certain extent, thereby improving the transmission efficiency between the drive shaft and the cam.

[0023] Optionally, a first groove is provided on the hole wall of the through hole; a second groove is provided on the main shaft; one end of the anti-slip member is received in the first groove, and the other end of the anti-slip member is received in the second groove.

[0024] For the above compression mechanism, by respectively providing a first groove on the hole wall and a second groove on the main shaft for receiving parts of the anti-slip member, both the principle and the implementation process are relatively simple, which improves the manufacturing convenience of the compression mechanism, and thus reduces the manufacturing cost of the compression mechanism.

[0025] Optionally, the compression mechanism includes a diaphragm compressor.

[0026] For the above compression mechanism, by applying the compression mechanism provided in the present application to a diaphragm compressor, the inertial torque brought by the reciprocating motion of the piston in the compression bodies symmetrically arranged in pairs to the entire compression mechanism is offset to a certain extent. Finally, the stability and reliability of the diaphragm compressor are improved.

[0027] In summary, for the compression mechanism provided in the present application, since the rim of the cam has at least two abutting points with unequal radii and different radial directions of the rotation trajectories, the reciprocating motions of the first piston and the second piston are driven. Through the design that the axial direction of the first piston rod is collinear with the axial direction of the second piston rod, the inertial torque brought by the two of them to the entire compression mechanism is offset to a certain extent, thereby improving the stability and reliability of the compression mechanism. By selecting an elliptical wheel as the cam and the rotation axis can pass through the center of the elliptical wheel, the first piston and the second piston can reciprocate synchronously, and thus the inertial torque brought by the reciprocating motions of the first piston and the second piston to the entire compression mechanism is almost completely offset, finally further improving the stability and reliability of the compression mechanism. Through the structural design of the first arc-shaped end face on the first piston rod and / or the structural design of the second arc-shaped end face on the second piston rod, the contact area between the first piston rod and / or the second piston rod and the cam rim is reduced, thereby reducing the friction force between the first piston rod and / or the second piston rod and the cam rim, improving the running smoothness of the compression mechanism, and reducing the energy consumption of the compression mechanism. Especially when the compression mechanism provided in the present application is applied to a diaphragm compressor, the inertial torque brought by the reciprocating motion of the piston in the compression bodies symmetrically arranged in pairs to the entire compression mechanism is offset to a certain extent. Finally, the stability and reliability of the diaphragm compressor are improved. Description of the Drawings

[0028] To more clearly illustrate the technical solutions of the embodiments of the present application, the following will briefly introduce the drawings required for the embodiments. It should be understood that the following drawings only show some embodiments of the present application and should not be regarded as limiting the scope. For those of ordinary skill in the art, without creative efforts, other related drawings can also be obtained based on these drawings.

[0029] Figure 1 The force analysis schematic diagram of the traditional compression mechanism provided by the embodiment of the present application;

[0030] Figure 2 The three-dimensional view of the compression mechanism provided by the embodiment of the present application;

[0031] Figure 3 The three-dimensional view of some components in the compression mechanism provided by the embodiment of the present application;

[0032] Figure 4 The exploded view of some components in the compression mechanism provided by the embodiment of the present application.

[0033] Icon: 200, compression mechanism; 210, first compression body; 211, first piston; 2111, first piston rod; 2112, first piston head; 2113, first arc end face; 2114, first piston head flange; 2115, first piston rod flange; 212, first clamping member; 220, second compression body; 221, second piston; 2211, second piston rod; 2212, second piston head; 2213, second arc end face; 2214, second piston head flange; 2215, second piston rod flange; 222, second clamping member; 230, cam; 231, cam body; 2311, through hole; 2312, first groove; 232, anti-slip member; 240, drive shaft; 241, second groove. Detailed implementation manners

[0034] To make the objectives, technical solutions, and advantages of the embodiments of the present application clearer, the following will clearly and completely describe the technical solutions in the embodiments of the present application with reference to the drawings in the embodiments of the present application. Obviously, the described embodiments are some, but not all, of the embodiments of the present application. Usually, the components of the embodiments of the present application described and shown in the drawings here can be arranged and designed in various different configurations.

[0035] Therefore, the following detailed description of the embodiments of the present application provided in the drawings is not intended to limit the scope of the present application to be protected, but only represents the selected embodiments of the present application. Based on the embodiments in the present application, all other embodiments obtained by those of ordinary skill in the art without creative efforts belong to the scope of protection of the present application.

[0036] It should be noted that like reference numerals and letters denote like items in the following figures, and thus, once an item is defined in one figure, it need not be further defined or explained in subsequent figures.

[0037] In the description of the present application, it should be noted that the orientation or positional relationship indicated by the terms "center", "upper", "lower", "left", "right", "vertical", "horizontal", "inner", "outer", etc. is based on the orientation or positional relationship shown in the figures, or the orientation or positional relationship in which the inventive product is customarily placed during use. It is only for the convenience of describing the present application 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 thus should not be construed as a limitation on the present application. In addition, the terms "first", "second", "third", etc. are only used for distinguishing descriptions and should not be construed as indicating or implying relative importance.

[0038] In addition, terms such as "horizontal" and "vertical" do not mean that the components are required to be absolutely horizontal or hanging vertically, but can be slightly inclined. For example, "horizontal" only means that its direction is more horizontal relative to "vertical", and does not mean that the structure must be completely horizontal, but can be slightly inclined.

[0039] In the description of the present application, it should also be noted that unless otherwise clearly specified and limited, the terms "arranged", "installed", "connected", and "coupled" should be understood in a broad sense. For example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be directly connected or indirectly connected through an intermediate medium, and it can be the communication inside two elements. For those of ordinary skill in the art, the specific meanings of the above terms in the present application can be understood according to specific circumstances.

[0040] At present, for the reciprocating compression mechanism as an example, a crankshaft connecting rod is usually arranged between two compression bodies, and the pistons in the two compression bodies are simultaneously driven to move when the crankshaft connecting rod rotates, thereby realizing the synchronous movement of the two pistons in opposite directions. However, as Figure 1 shown, this way of arranging the crankshaft connecting rod makes the two pistons unable to be collinear, and thus the movement directions of the two pistons are not collinear. Under the action of the inertial forces in these two opposite but non-collinear movement directions, the entire compression mechanism usually generates an inertial moment. This inertial moment causes the entire compression mechanism to have a tendency to rotate. Under this rotation tendency, the stability and reliability of the compressor mechanism will be greatly reduced.

[0041] In view of this, the present application provides a compression mechanism to solve the above technical problems. Specifically, please refer to the embodiments and figures provided in the present application.

[0042] Please refer toFigure 2 , Figure 2 is a perspective view of the compression mechanism 200 provided by an embodiment of the present application. The compression mechanism 200 provided by an embodiment of the present application may include a first compression body 210, a second compression body 220, and a rotatable cam 230. The first compression body 210 may include a first piston 211, and the first piston 211 may include a first piston rod 2111 and a first piston head 2112. The second compression body 220 may include a second piston 221, and the second piston 221 may have a second piston rod 2211 and a second piston head 2212. The cam 230 may be configured to rotate along a rotation axis when being driven. Wherein, the rotation axis may be perpendicular to the plane where the cam 230 is located. One end of the first piston rod 2111 away from the first piston head 2112 and one end of the second piston rod 2211 away from the second piston head 2212 may respectively abut against the rim of the cam 230. The axial direction of the first piston rod 2111 may be collinear with the axial direction of the second piston rod 2211, and may be parallel to the plane where the cam 230 is located. There may be at least two abutting points on the rim with unequal radii of rotation trajectories. Wherein, different abutting points may be different in the radial direction of the cam 230.

[0043] The compression of the first compression body 210 may be completed by the movement of the first piston 211; the compression of the second compression body 220 may be completed by the movement of the second piston 221. The cam 230 may rotate under the rotation action of the drive shaft 240. Its rim respectively abuts against one end of the first piston rod 2111 away from the first piston head 2112 and one end of the second piston rod 2211 away from the second piston head 2212. The cam 230 may be circular, may also be elliptical, or may also be of other shapes, such as non-square rhombus, other polygons, etc.

[0044] Regarding the cam 230 having at least two abutting points with unequal radii of rotation trajectories, and the abutting points being different in the radial direction of the cam 230, it means that there are at least two abutting points with different radial directions on the cam 230, and the distances from the rotation axis are unequal.

[0045] Exemplarily, if the cam 230 is circular and the rotation axis is located at its center, then for any two points with different radial directions on the rim of the circular cam 230, the radii of the rotation trajectories between them are the same. That is, there are no at least two abutting points on the rim of the circular cam 230 with unequal radii of rotation trajectories and different radial directions. If the rotation axis of the circular cam 230 is eccentrically arranged, then for any two points with different radial directions on the rim of the circular cam 230, the radii of the rotation trajectories between them are different. That is, there are countless abutting points on the rim of the circular cam 230 with unequal radii of rotation trajectories and different radial directions.

[0046] Furthermore, it should be understood that if the cam 230 is an ellipse, a non-special rhombus, or other polygon, etc., regardless of whether the rotation axis is located at its geometric center, the rim of the cam 230 has at least two abutting points with unequal radii of rotation trajectories and different radial directions.

[0047] During the operation of the compression mechanism 200, the cam 230 rotates when driven. When one end of the first piston rod 2111 away from the first piston head 2112 and one end of the second piston rod 2211 away from the second piston head 2212 respectively abut against the rim of the cam 230, since the rim of the cam 230 has at least two abutting points with unequal radii of rotation trajectories and different radial directions, the distances of one end of the first piston rod 2111 away from the first piston head 2112 and one end of the second piston rod 2211 away from the second piston head 2212 from the rotation axis will change as the cam 230 rotates. Furthermore, the reciprocating motion of the first piston 211 and the second piston 221 can be achieved.

[0048] Exemplarily again, if the cam 230 is an elliptical wheel and the rotation center is located at the center of the elliptical wheel, when one end of the first piston rod 2111 away from the first piston head 2112 and one end of the second piston rod 2211 away from the second piston head 2212 respectively abut against the abutting points on the minor axis of the elliptical wheel, as the ellipse rotates, the abutting points on the ellipse where one end of the first piston rod 2111 away from the first piston head 2112 and one end of the second piston rod 2211 away from the second piston head 2212 abut will become the abutting points on the major axis of the elliptical wheel. During this process, since the distances of the abutting points on the elliptical wheel being abutted from the rotation axis increase, the first piston 211 and the second piston 221 also move in the direction of shrinking the compression space, thereby achieving the compression of the substance to be compressed.

[0049] Correspondingly, when one end of the first piston rod 2111 away from the first piston head 2112 and one end of the second piston rod 2211 away from the second piston head 2212 respectively abut against the abutting points on the major axis of the elliptical wheel, as the ellipse rotates, the abutting points on the ellipse where one end of the first piston rod 2111 away from the first piston head 2112 and one end of the second piston rod 2211 away from the second piston head 2212 abut will become the abutting points on the minor axis of the elliptical wheel. During this process, since the distances of the abutting points on the elliptical wheel being abutted from the rotation axis shorten, the first piston 211 and the second piston 221 will rebound under the pressure of the first compression body 210 and the second compression body 220 respectively, causing one end of the first piston rod 2111 away from the first piston head 2112 and one end of the second piston rod 2211 away from the second piston head 2212 to approach the elliptical wheel and abut against its rim respectively. By cycling in this way, the reciprocating motion of the first piston 211 and the second piston 221 can be achieved.

[0050] It should be understood that the shape of the cam 230 and the position of the rotation axis determine whether the first piston 211 and the second piston 221 can reciprocate synchronously. For example, an elliptical wheel with the rotation axis at the center of the ellipse can usually achieve synchronous reciprocating motion of the first piston 211 and the second piston 221; a circular cam 230 with an eccentric rotation axis usually cannot achieve synchronous reciprocating motion of the first piston 211 and the second piston 221. However, regardless of whether the first piston 211 and the second piston 221 can reciprocate synchronously, since their piston movement directions are opposite and collinear, when the cam 230 rotates, it can still offset the inertia torques brought by the two to the entire compression mechanism 200 to a certain extent. That is, because the movement directions of the first piston 211 and the second piston 221 are opposite and collinear, there is usually no inertia torque between the inertia forces they bring to the entire compression mechanism 200.

[0051] It is worth mentioning that the compression mechanism 200 provided in the embodiment of the present application may further include symmetrically arranged third compression bodies and fourth compression bodies, symmetrically arranged fifth compression bodies and sixth compression bodies, etc.

[0052] In the above implementation process, since the rim of the cam 230 has at least two abutting points with unequal radii and different radial directions of the rotation trajectories, the reciprocating motion of the first piston 211 and the second piston 221 is driven. On this basis, through the design that the axial direction of the first piston rod 2111 is collinear with the axial direction of the second piston rod 2211, the inertia torques brought by the two to the entire compression mechanism 200 are offset to a certain extent. That is, because the movement directions of the first piston 211 and the second piston 221 are opposite and collinear, there is usually no inertia torque between the inertia torques they bring to the entire compression mechanism 200. Furthermore, the stability and reliability of the compression mechanism 200 are improved.

[0053] Please continue to refer to Figure 2 , in some alternative embodiments, the cam 230 may include an elliptical wheel.

[0054] In the above implementation process, using the elliptical wheel as the cam 230 does not require considering whether the rotation axis is eccentrically arranged as when selecting a circular wheel as the cam 230, and thus drives the reciprocating motion of the first piston 211 and the second piston 221. That is, using the elliptical wheel as the cam 230 makes the selection of the rotation axis position more flexible.

[0055] Please continue to refer to Figure 2 , in some alternative embodiments, the rotation axis of the elliptical wheel may pass through the center of the elliptical wheel.

[0056] As can be seen from the examples listed in the previous embodiments, using an elliptical wheel as the cam 230 with the axis of rotation passing through the center of the elliptical wheel enables the first piston 211 and the second piston 221 to perform reciprocating motions synchronously.

[0057] In the above implementation process, by selecting an elliptical wheel as the cam 230 with the axis of rotation passing through the center of the elliptical wheel, the first piston 211 and the second piston 221 are enabled to perform reciprocating motions synchronously. Furthermore, the inertial torques brought by the reciprocating motions of the first piston 211 and the second piston 221 to the entire compression mechanism 200 are almost completely offset. Finally, the stability and reliability of the compression mechanism 200 are further improved.

[0058] Please combine Figure 2 with reference to Figure 3 , Figure 3 which is a perspective view of some components in the compression mechanism 200 provided by the embodiment of the present application. In some alternative embodiments, one end of the first piston rod 2111 away from the first piston head 2112 may have a first arc-shaped end face 2113. The first arc-shaped end face 2113 may be curved towards the first piston head 2112, and the bending direction may be parallel to the plane where the cam 230 is located. The first arc-shaped end face 2113 may abut against the rim of the cam 230.

[0059] And / or one end of the second piston rod 2211 away from the second piston head 2212 may have a second arc-shaped end face 2213. The second arc-shaped end face 2213 may be curved towards the second piston head 2212, and the bending direction may be parallel to the plane where the cam 230 is located. The second arc-shaped end face 2213 may abut against the rim of the cam 230.

[0060] In other words, the arching directions of the first arc-shaped end face 2113 and the second arc-shaped end face are both parallel to the plane where the cam 230 is located.

[0061] In the above implementation process, when one end of the first piston rod 2111 away from the first piston head 2112 and one end of the second piston rod 2211 away from the second piston head 2212 respectively abut against the rim of the cam 230, relative sliding will occur between the rim of the cam and one end of the first piston rod 2111 away from the first piston head 2112 and one end of the second piston rod 2211 away from the second piston head 2212 during the rotation of the cam wheel.

[0062] Please continue to refer to Figure 2 and Figure 3 , in some alternative embodiments, the first piston head 2112 may be detachably connected to the first piston rod 2111. And / or the second piston head 2212 may be detachably connected to the second piston rod 2211.

[0063] The detachable connection described above can be in the forms of screw connection, snap connection, pin connection, etc.

[0064] In the above implementation process, through the detachable connection between the first piston head 2112 and the first piston rod 2111 and / or the detachable connection between the second piston head 2212 and the second piston rod 2211, in the case of a failure of the first piston head 2112, the first piston rod 2111 and / or the second piston head 2212, the second piston rod 2211, it is not necessary to replace the first piston 211 and / or the second piston 221 as a whole. Thus, the maintenance cost of the compression mechanism 200 is reduced.

[0065] Please continue to refer to Figure 2 and Figure 3 , in some alternative embodiments, the first piston head 2112 facing the first piston rod 2111 may have a first piston head flange 2115. One end of the first piston rod 2111 facing the first piston head 2112 may have a first piston rod flange 2215. The first piston head flange 2115 and the first piston rod flange 2215 may be connected by a first fastener.

[0066] and / or the second piston head 2212 facing the second piston rod 2211 may have a second piston head flange 2214. One end of the second piston rod 2211 facing the second piston head 2212 may have a second piston rod flange 2215. The second piston head flange 2214 and the second piston rod flange 2215 may be connected by a second fastener.

[0067] Both the first fastener and the second fastener may be bolts.

[0068] In the above implementation process, the first piston head 2112 and the first piston rod 2111 are connected by a flange, and / or the second piston head 2212 and the second piston rod 2211 are connected by a flange, which improves the disassembly convenience and installation stability between the first piston head 2112 and the first piston rod 2111, and / or between the second piston head 2212 and the second piston rod 2211.

[0069] Please continue to refer to Figure 2 , in some alternative embodiments, the first compression body 210 may be provided with a first clamping member 212. The first clamping member 212 can clamp the first piston rod 2111 and can be configured to limit the movement direction of the first piston rod 2111 to the axial direction of the first piston rod 2111.

[0070] and / or the second compression body 220 may be provided with a second clamping member 222. The second clamping member 222 can clamp the second piston rod 2211 and can be configured to limit the movement direction of the second piston rod 2211 to the axial direction of the second piston rod 2211.

[0071] Since the first piston rod 2111 abuts against the flange of the cam 230, during the rotation of the cam 230, the frictional force between the cam 230 and the first piston rod 2111 usually causes the first piston rod 2111 to swing. Therefore, by clamping the first piston rod 2111 with the first clamping member 212, the swing of the first piston rod 2111 can be prevented to a certain extent.

[0072] Correspondingly, since the second piston rod 2211 abuts against the flange of the cam 230, during the rotation of the cam 230, the frictional force between the cam 230 and the second piston rod 2211 usually causes the second piston rod 2211 to swing. Therefore, by clamping the second piston rod 2211 with the second clamping member 222, the swing of the second piston rod 2211 can be prevented to a certain extent.

[0073] In the above implementation process, by clamping the first piston rod 2111 with the first clamping member 212 and / or clamping the second piston rod 2211 with the second clamping member 222, the swing of the first piston rod 2111 and / or the second piston rod 2211 is limited to a certain extent, thereby further improving the stability and reliability of the compression mechanism 200.

[0074] Please refer to Figure 2 and Figure 4 , Figure 4 which is an exploded view of some components in the compression mechanism 200 provided by the embodiment of the present application. In some alternative embodiments, the compression mechanism 200 may further include a drive shaft 240. The cam 230 may include a cam 230 body and an anti-slip member 232. A through hole 2311 may be provided on the cam 230 body. The drive shaft 240 may pass through the through hole 2311. One end of the anti-slip member 232 may be connected to the hole wall of the through hole 2311, and the other end may be connected to the drive shaft 240. The axial direction of the drive shaft 240 may be parallel to the rotation axis and may be configured to drive the cam 230 to rotate when it rotates.

[0075] Generally, the drive shaft 240 is a cylindrical shaft. Therefore, if a through hole 2311 is directly formed on the cam 230 and sleeved on the drive shaft 240, slipping usually occurs between the cam 230 and the drive shaft 240. By connecting the cam 230 and the drive shaft 240 respectively at both ends of the anti-slip member 232, the slipping between the cam 230 and the drive shaft 240 can be prevented to a certain extent.

[0076] In the above implementation process, by providing the anti-slip member 232 between the cam 230 and the drive shaft 240, the slipping between the cam 230 and the drive shaft 240 is prevented to a certain extent, thereby improving the transmission efficiency between the drive shaft 240 and the cam 230.

[0077] Please continue to refer to Figure 2 andFigure 4 , in some alternative embodiments, a first groove 2312 may be provided on the hole wall of the through hole 2311. A second groove 241 may be provided on the main shaft. One end of the anti-slip member 232 may be received in the first groove 2312, and the other end of the anti-slip member 232 may be received in the second groove 241.

[0078] In the above implementation process, by respectively providing the first groove 2312 on the hole wall and the second groove 241 on the main shaft for receiving the anti-slip member 232, both the principle and the implementation process are relatively simple, improving the manufacturing convenience of the compression mechanism 200 and thus reducing the manufacturing cost of the compression mechanism 200.

[0079] In some alternative embodiments, the compression mechanism 200 may include a diaphragm compressor.

[0080] In the above implementation process, by applying the compression mechanism 200 provided in the present application to the diaphragm compressor, to a certain extent, the inertia torque brought to the entire compression mechanism 200 by the piston reciprocating motion in the diaphragm compressor arranged symmetrically in pairs is offset. Ultimately, the stability and reliability of the diaphragm compressor are improved.

[0081] In summary, for the compression mechanism 200 provided in each embodiment of the present application, since the rim of the cam 230 has at least two abutting points with unequal radii and different radial directions of the rotation trajectories, the reciprocating motions of the first piston 211 and the second piston 221 are driven. Through the design that the axial direction of the first piston rod 2111 is collinear with the axial direction of the second piston rod 2211, the inertial moments brought by the two for the entire compression mechanism 200 are offset to a certain extent, thereby improving the stability and reliability of the compression mechanism 200. By selecting an elliptical wheel as the cam 230 and the rotation axis can pass through the center of the elliptical wheel, it is realized that the first piston 211 and the second piston 221 can reciprocate synchronously, and thus the inertial moments brought by the reciprocating motions of the first piston 211 and the second piston 221 for the entire compression mechanism 200 are almost completely offset, ultimately further improving the stability and reliability of the compression mechanism 200. Through the structural design of the first arc-shaped end face 2113 on the first piston rod 2111 and / or the structural design of the second arc-shaped end face 2213 on the second piston rod 2211, the contact area between the first piston rod 2111 and / or the second piston rod 2211 and the rim of the cam 230 is reduced, thereby reducing the frictional force between the first piston rod 2111 and / or the second piston rod 2211 and the rim of the cam 230, improving the running smoothness of the compression mechanism 200, and reducing the energy consumption of the compression mechanism 200. In particular, when the compression mechanism 200 provided in the present application is applied to a diaphragm compressor, the inertial moments brought by the piston reciprocating motions in the diaphragm compressor symmetrically arranged in pairs for the entire compression mechanism 200 are offset to a certain extent. Finally, the stability and reliability of the diaphragm compressor are improved.

[0082] The foregoing is only a preferred embodiment of the present application and is not intended to limit the present application. For those skilled in the art, the present application may have various changes and modifications. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present application shall be included in the protection scope of the present application.

Claims

1. A compression mechanism, characterized in that, Comprising a first compression body, a second compression body and a rotatable cam; The first compression body includes a first piston, and the first piston includes a first piston rod and a first piston head; the second compression body includes a second piston, and the second piston has a second piston rod and a second piston head; The cam is configured to rotate along a rotation axis when being driven; wherein, the rotation axis is perpendicular to the plane where the cam is located; One end of the first piston rod away from the first piston head and one end of the second piston rod away from the second piston head respectively abut against the rim of the cam; The axial direction of the first piston rod is collinear with the axial direction of the second piston rod and is parallel to the plane where the cam is located; There are at least two abutting points on the rim with unequal radii of rotation trajectories; wherein, different abutting points are different in the radial direction of the cam.

2. The compression mechanism according to claim 1, wherein The cam includes an elliptical wheel.

3. The compression mechanism according to claim 2, wherein, The rotation axis of the elliptical wheel passes through the center of the elliptical wheel.

4. The compression mechanism according to claim 1, characterized in that One end of the first piston rod away from the first piston head has a first arc-shaped end face; the first arc-shaped end face bends towards the first piston head, and the bending direction is parallel to the plane where the cam is located; the first arc-shaped end face abuts against the rim of the cam; and / or One end of the second piston rod away from the second piston head has a second arc-shaped end face; the second arc-shaped end face bends towards the second piston head, and the bending direction is parallel to the plane where the cam is located; the second arc-shaped end face abuts against the rim of the cam.

5. The compression mechanism according to claim 1, characterized in that, The first piston head is detachably connected to the first piston rod; and / or The second piston head is detachably connected to the second piston rod.

6. The compression mechanism according to claim 5, wherein, The first piston head has a first piston head flange towards the first piston rod; one end of the first piston rod towards the first piston head has a first piston rod flange; the first piston head flange and the first piston rod flange are connected by a first fastener; and / or The second piston head has a second piston head flange towards the second piston rod; one end of the second piston rod towards the second piston head has a second piston rod flange; the second piston head flange and the second piston rod flange are connected by a second fastener.

7. The compression mechanism according to claim 1, characterized in that The compression mechanism further includes a drive shaft; The cam includes a cam body and an anti-slip member; A through hole is provided on the cam body; The drive shaft passes through the through hole, one end of the anti-slip member is connected to the hole wall of the through hole, and the other end is connected to the drive shaft; The axial direction of the drive shaft is parallel to the rotation axis and is configured to drive the cam to rotate when it rotates.

8. The compression mechanism according to claim 7, characterized in that, A first groove is provided on the hole wall of the through hole; A second groove is provided on the main shaft; The first groove accommodates one end of the anti-slip member, and the second groove accommodates the other end of the anti-slip member.

9. The compression mechanism according to any one of claims 1 to 8, characterized in that, The compression mechanism includes a diaphragm compressor.

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