CN118346560A - Linear reciprocating mechanism and compression device - Google Patents

Abstract

The application relates to a linear reciprocating mechanism and a compression device, wherein the linear reciprocating mechanism comprises a rotary transmission part, a reciprocating body and a first rolling part, a first guide groove is formed in the circumferential surface of the rotary transmission part, the track of the first guide groove is a closed curve encircling the rotary transmission part for a circle, and the reciprocating body is provided with a first installation part; the first rolling element is arranged on the first installation part and matched with the first guide groove; when the rotary transmission member rotates, the first rolling member moves along the first guide groove to drive the reciprocating body to reciprocate along the axial direction of the rotary transmission member, the reciprocating motion stroke of the reciprocating body is L, the distance from the center of the first rolling member to the center line of the rotary transmission member is R, and the value range of R/L is 1-8. According to the linear reciprocating mechanism and the compression device, the reciprocating motion rhythm of the reciprocating body is matched with the radius of the rotary transmission part, so that the sine curve of the track of the first guide groove is smooth, the stability of reciprocating motion is improved, and the compression efficiency is ensured.

Description

Linear reciprocating mechanism and compression device

Technical Field

The application relates to the technical field of compressors, in particular to a linear reciprocating motion mechanism and a compression device.

Background

A compressor is a driven fluid machine that lifts low pressure gas to high pressure gas. In the compressor, the reciprocating motion of the piston in the cylinder body is generally utilized to realize pumping fluid and compressing fluid, so that a gas valve is needed to be utilized to allocate on-off of a gas path.

In the related art, during the reciprocating motion process of the linear reciprocating motion mechanism, clamping stagnation or thrust deviating from the axis is easy to occur, so that the movement rhythm of the piston during the reciprocating motion in the cylinder body is easy to be disturbed, and the compression effect is low.

Disclosure of Invention

Accordingly, it is necessary to provide a linear reciprocating mechanism and a compression device for solving the problem that the compression efficiency is low due to the disturbance of the reciprocating rhythm of the piston.

In one aspect, the present application provides a linear reciprocating mechanism comprising:

the device comprises a rotary transmission part, wherein a first guide groove is formed in the circumferential surface of the rotary transmission part, the track of the first guide groove is a closed curve encircling the rotary transmission part for a circle, and the closed curve is a sine curve;

a reciprocating body provided with a first mounting portion;

The first rolling piece is arranged on the first mounting part and matched with the first guide groove;

when the rotary transmission member rotates, the first rolling member moves along the first guide groove to drive the reciprocating body to reciprocate along the axial direction of the rotary transmission member, the reciprocating motion stroke of the reciprocating body is L, the distance from the center of the first rolling member to the center line of the rotary transmission member is R, and the value range of R/L is 1-8.

In one embodiment, the circumferential surface of the rotary transmission member is provided with a second guide groove, tracks of the first guide groove and the second guide groove are sinusoidal with the same amplitude, the first guide groove and the second guide groove are arranged along the axial direction of the rotary transmission member at intervals, peaks in the track of the first guide groove and peaks in the track of the second guide groove are staggered in the circumferential direction of the rotary transmission member, the reciprocating body is provided with a second installation part which is relatively fixed with the first installation part, the second installation part is used for installing a second rolling member, the second rolling member is matched with the second guide groove, when the rotary transmission member rotates, the first rolling member moves along the first guide groove, the second rolling member moves along the second guide groove, and displacement variation of the first rolling member and the second rolling member in the axial direction of the rotary transmission member is equal.

In one embodiment, the number of the first rolling elements and the number of the second rolling elements are 2, and the connecting lines of the 2 first rolling elements and the connecting lines of the 2 second rolling elements are perpendicular to the central line of the rotary transmission element.

In one embodiment, the linear reciprocating mechanism further comprises a base, a box body and a guide assembly, the box body is connected with the base to enclose to form a movable space, the rotary transmission part, the reciprocating body and the guide assembly are all arranged in the movable space, the rotary transmission part is axially limited to the base, and when the rotary transmission part rotates relative to the base, the reciprocating body is driven by the rotary transmission part to reciprocate in the movable space along the guide assembly.

In one embodiment, the base is rotatably provided with a rotating member, the rotating member is connected with the rotating transmission member, and the rotating member is used for driving the rotating transmission member to rotate relative to the base.

On the other hand, the application provides a compression device, which comprises a compression cylinder and the linear reciprocating mechanism, wherein the compression cylinder comprises a cylinder body and a piston, the cylinder body is provided with a volume cavity, the piston is arranged in the volume cavity, the piston is connected with the reciprocating body, and when the rotary transmission part rotates, the piston is driven by the reciprocating body to do reciprocating motion.

In one embodiment, the compression device comprises a first shell and a first valve plate assembly, the first shell is provided with a first air inlet and a first air outlet, the first valve plate assembly is clamped between the cylinder body and the first shell, the first valve plate assembly comprises a valve plate, a first valve plate, a pressing plate and a second valve plate, a first mounting groove, a second mounting groove, a first air passage and a second air passage are formed in the valve plate, the first air passage penetrates to the bottom of the first mounting groove, the second air passage penetrates to the bottom of the second mounting groove, the first valve plate is arranged in the first mounting groove, a part of the first valve plate is closed to the first air passage, the pressing plate is arranged in the second mounting groove, a third air passage is formed in the pressing plate, the second valve plate is clamped between the valve plate and the pressing plate, a part of the second valve plate is closed to the third air passage, when the piston moves relatively to the cylinder body in the first direction, the first air passage penetrates to the bottom of the second mounting groove, the first air passage is closed to the first air passage, the first air passage is arranged in the second air passage in the first direction opposite to the first direction, and the second air passage is discharged relatively to the second air passage in the first direction from the first air passage and the second direction.

In one embodiment, the first valve plate and the second valve plate each comprise a covering portion and an elastic portion, both sides of the elastic portion are respectively arranged on the covering portion through separation grooves, both ends of the elastic portion are respectively connected with the covering portion, and the elastic portion can elastically deform relative to the covering portion under thrust of air flow.

In one embodiment, the cylinder body is in sealing fit with the valve plate, and the first shell is in sealing fit with the valve plate and/or the cylinder body.

In one embodiment, the compression device further comprises a second shell, the first shell and the second shell are respectively connected to two sides of the cylinder body, the piston divides the volume cavity into a first volume cavity and a second volume cavity, the first volume cavity is located between the first shell and the piston, the second volume cavity is located between the second shell and the piston, the second shell is provided with a second air inlet and a second air outlet, the compression cylinder comprises a second valve plate assembly, the second valve plate assembly has the same structure as the first valve plate assembly, and the second valve plate assembly is clamped between the cylinder body and the second shell; when the piston moves towards a first direction relative to the cylinder body, the first air inlet pumps air into the first containing cavity through the first air passage of the first valve plate assembly, and the piston discharges the air in the second containing cavity from the second air outlet through the second air passage and the third air passage of the second valve plate assembly; when the piston moves towards the second direction relative to the cylinder body, the second air inlet pumps air into the second containing cavity through the first air passage of the second valve plate assembly, and the piston discharges the air in the first containing cavity from the first air outlet through the second air passage and the third air passage of the first valve plate assembly.

According to the linear reciprocating mechanism and the compression device, when the rotary transmission piece rotates, the first rolling piece moves along the first guide groove, so that the rotary motion of the rotary transmission piece is converted into the axial reciprocating motion of the reciprocating body along the rotary transmission piece, and therefore the thrust deviating from the axis in the reciprocating motion process is avoided, meanwhile, the reciprocating motion rhythm of the reciprocating body is matched with the size (such as the radius of the rotary transmission piece) of the rotary transmission piece while the transmission efficiency is ensured because the value range of the distance ratio between the reciprocating motion stroke of the reciprocating body and the center of the first rolling piece and the center line of the rotary transmission piece is 1-8, the track sinusoidal curve of the first guide groove is smooth, the reciprocating motion stability is improved, and the reciprocating motion rhythm of the piston is not easy to be disturbed when the reciprocating body is utilized to drive the piston to reciprocate, so that the compression efficiency is ensured.

Drawings

In order to more clearly illustrate the embodiments of the present application or the technical solutions in the related art, the drawings that are required to be used in the embodiments or the related technical descriptions will be briefly described, and it is apparent that the drawings in the following description are only some embodiments of the present application, and other embodiments of the drawings may be obtained according to the drawings without inventive effort to those of ordinary skill in the art.

Fig. 1 is a schematic cross-sectional view of a compression apparatus according to another embodiment of the present application.

Fig. 2 is a schematic view of the compression device shown in fig. 1, with the piston in another position.

Fig. 3 is a schematic cross-sectional structure of a compression cylinder according to an embodiment of the present application, in which a dotted arrow shows a gas path when the compression cylinder is intake.

Fig. 4 is a schematic view of the gas path of the compression cylinder shown in fig. 3 at the time of exhaust.

Fig. 5 is a schematic view showing an assembly structure of a linear reciprocating mechanism of a compressing apparatus according to an embodiment of the present application.

Fig. 6 is an exploded view of a linear reciprocating mechanism of a compressing apparatus according to an embodiment of the present application.

Fig. 7 is a schematic view showing the installation positions of the first rolling element and the second rolling element of the linear reciprocating mechanism relative to the reciprocating body in the compressing apparatus according to the embodiment of the present application.

Fig. 8 is a schematic structural view of a rotary transmission member of a linear reciprocating mechanism in a compression apparatus according to an embodiment of the present application.

Fig. 9 is a schematic view showing another view of a rotary driving member of a linear reciprocating mechanism in a compressing apparatus according to an embodiment of the present application.

Fig. 10 is an exploded view of a valve plate assembly according to an embodiment of the present application.

Fig. 11 is a schematic structural view of a first housing of a compression cylinder according to an embodiment of the present application.

Fig. 12 is a schematic structural view of a compression cylinder according to another embodiment of the present application.

Fig. 13 is an exploded structural view of the compression cylinder shown in fig. 12.

Fig. 14 is a schematic perspective view showing a sectional structure of a compression cylinder according to an embodiment of the present application.

Reference numerals illustrate:

100. A valve plate assembly; 100a, a first valve plate assembly; 100b, a second valve plate assembly; 1. a valve plate; 1a, a first mounting groove; 1b, a second mounting groove; 1c, a first air passage; 1d, a second air passage; 1e, an empty-avoiding groove; 2. a first valve plate; 3. a pressing plate; 3a, a third air passage; 4. a second valve plate; t, a pasting part; q, elastic part; G. a separation groove; 5. a first seal ring; 6. a second seal ring;

1001. A compression cylinder; 101. a cylinder; 1011. a volume chamber; 1011a, a first cavity; 1011b, a second cavity; 1012. a heat radiation fin; 102. a piston; 103. a piston rod; 104. a first housing; 104a, a first air inlet; 104b, a first air outlet; 104c, an air inlet cavity; 104d, an exhaust chamber; 104e, a separator; 105. a first seal; 106. a second seal; 107. a third seal; 108. a second housing; 108a, a second air inlet; 108b, a second air outlet; 1001a, first direction; 1001b, second direction;

1002. A linear reciprocating mechanism; 10a, a base; 11. a rotary transmission member; 11a, a first guide groove; 11b, a second guide groove; 111. a mounting hole; 112. a clamping protrusion; 12. a reciprocating body; 12a, a first mounting part; 12b, a second mounting portion; 12c, a linear bearing; 121. a mounting groove; 122. a ball sleeve; 123. a ball; 124. a cover; 13. a first rolling member; 14. a second rolling member; 14a, a first planar bearing; 14b, a second planar bearing; 14c, a first rolling bearing; 14d, a second rolling bearing; 141. a through hole; 141a, a necking section; 141b, a first step groove; 141c, a second step groove; 15. a case; 15a, a shaft hole; 16.a guide assembly; 16a, a guide rod; 17. a rotating member; 171. a rotating disc; 172. a rotating shaft; 18. a bushing; 19. a Gelai circle; 1000. compression device.

Detailed Description

In order that the above objects, features and advantages of the application will be readily understood, a more particular description of the application will be rendered by reference to the appended drawings. In the following description, numerous specific details are set forth in order to provide a thorough understanding of the present application. The present application may be embodied in many other forms than described herein and similarly modified by those skilled in the art without departing from the spirit of the application, whereby the application is not limited to the specific embodiments disclosed below.

In the description of the present application, it should be understood that, if any, these terms "center", "longitudinal", "transverse", "length", "width", "thickness", "upper", "lower", "top", "bottom", "inner", "outer", "axial", "radial", "circumferential", etc., are used in the description of the present application, these terms refer to the orientation or positional relationship based on the orientation or positional relationship shown in the drawings, only for convenience of describing the present application and simplifying the description, and do not indicate or imply that the apparatus or elements referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be construed as limiting the present application.

Furthermore, the terms "first," "second," and the like, if any, are used for descriptive purposes only and are not to be construed as indicating or implying a relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defining "a first" or "a second" may explicitly or implicitly include at least one such feature. In the description of the present application, the terms "plurality" and "a plurality" if any, mean at least two, such as two, three, etc., unless specifically defined otherwise.

In the present application, unless explicitly stated and limited otherwise, the terms "mounted," "connected," "secured," and the like are to be construed broadly. For example, the two parts can be fixedly connected, detachably connected or integrated; can be mechanically or electrically connected; either directly or indirectly, through intermediaries, or both, may be in communication with each other or in interaction with each other, unless expressly defined otherwise. The specific meaning of the above terms in the present application can be understood by those of ordinary skill in the art according to the specific circumstances.

In the present application, unless expressly stated or limited otherwise, the meaning of a first feature being "on" or "off" a second feature, and the like, is that the first and second features are either in direct contact or in indirect contact through an intervening medium. Moreover, a first feature being "above," "over" and "on" a second feature may be a first feature being directly above or obliquely above the second feature, or simply indicating that the first feature is level higher than the second feature. The first feature being "under", "below" and "beneath" the second feature may be the first feature being directly under or obliquely below the second feature, or simply indicating that the first feature is less level than the second feature.

Referring to fig. 1 and 2, a compression apparatus 1000 is provided according to an embodiment of the present application. The compression device 1000 includes a compression cylinder 1001 and a linear reciprocating mechanism 1002.

As shown in fig. 3 and 4, the compression cylinder 1001 includes a cylinder body 101 and a piston 102, the cylinder body 101 having a volume chamber 1011, the piston 102 being provided in the volume chamber 1011.

The linear reciprocating mechanism 1002 is used to drive the piston 102 to reciprocate within the volume 1011.

As shown in connection with fig. 5 and 6, in some embodiments, the linear reciprocating mechanism 1002 includes a rotary transmission member 11, a reciprocating body 12, a first rolling member 13, and a second rolling member 14. The peripheral surface of the rotary transmission member 11 is provided with a first guide groove 11a and a second guide groove 11b. The first guide groove 11a and the second guide groove 11b are arranged at intervals along the axial direction of the rotary transmission member 11, and the tracks are closed curves around the rotary transmission member 11 for one circle. The reciprocating body 12 is provided with a first mounting portion 12a and a second mounting portion 12b which are relatively fixed. The first mounting portion 12a and the second mounting portion 12b are for mounting the first rolling member 13 and the second rolling member 14, respectively. It is to be understood that the first mounting portion 12a may be plural in number, thereby satisfying the need for mounting plural first rolling members 13. Accordingly, the number of the second mounting portions 12b may be plural to accommodate the need for mounting the plurality of second rolling members 14.

The first rolling member 13 is provided at the first mounting portion 12a and cooperates with the first guide groove 11 a. The second rolling member 14 is provided at the second mounting portion 12b and cooperates with the second guide groove 11 b. The first rolling element 13 and the first guide groove 11a are in rolling fit, and the second rolling element 14 and the second guide groove 11b are in rolling fit, so that friction force when the first rolling element 13 moves along the first guide groove 11a and friction force when the second rolling element 14 moves along the second guide groove 11b can be reduced, and smoothness of reciprocating motion of the reciprocating body 12 in the linear reciprocating motion mechanism 1002 is improved.

The reciprocating movement of the reciprocating body 12 can be achieved by providing one of the first rolling member 13 and the second rolling member 14. Accordingly, when only the first rolling member 1313 or only the second rolling member 1414 is provided, only the corresponding first guide groove 11a or second guide groove 11b is provided on the rotary transmission member 11. The reciprocating body 12 only needs to be provided with the corresponding first mounting portion 12a or second mounting portion 12b.

In the linear reciprocating mechanism 1002 of the present application, when the rotary transmission member 11 rotates, the first rolling member 13 moves along the first guide groove 11a to drive the reciprocating body 12 to reciprocate in the axial direction of the rotary transmission member 11, the reciprocating stroke of the reciprocating body 12 (i.e., the moving distance from one end limit position to the other end limit position during the reciprocating movement of the reciprocating body 12) is L, the distance from the center of the first rolling member 13 to the center line of the rotary transmission member 11 is R, and the value of R/L ranges from 1 to 8. In this embodiment, when the rotary transmission member 11 rotates, the first rolling member 13 moves along the first guide groove 11a, so as to convert the rotary motion of the rotary transmission member 11 into the axial reciprocating motion of the reciprocating body 12 along the rotary transmission member 11, thereby avoiding the occurrence of a thrust deviating from the axis in the reciprocating motion process, and meanwhile, as the value range of the ratio of the reciprocating motion stroke of the reciprocating body 12 to the distance from the center of the first rolling member 13 to the center line of the rotary transmission member 11 is 1 to 8, the transmission efficiency is ensured, and meanwhile, the reciprocating motion rhythm of the reciprocating body 12 is matched with the size (such as the radius of the rotary transmission member 11) of the rotary transmission member 11, so that the sinusoidal curve of the track of the first guide groove 11a is smooth, thereby facilitating the improvement of the reciprocating motion stability, and as such, when the reciprocating body 12 drives the piston 102 to reciprocate, the reciprocating motion rhythm of the piston 102 is not easy to be disturbed, and the compression efficiency is ensured.

Since the first rolling member 13 is moved along the first guide groove 11a while the first guide groove 11a is provided around the peripheral side of the rotary transmission member 11, the distance from the center of the first rolling member 13 to the center line of the rotary transmission member 11 can be regarded as the radius of the trajectory of the movement of the first rolling member 13 around the peripheral side of the rotary transmission member 11. Because the closed curve presented by the track of the first guide groove 11a is sinusoidal, when the value range of R/L is 1-8, the sinusoidal curve presented by the track of the first guide groove 11a has good smoothness, which is beneficial to guiding the smooth movement of the first rolling element 13, and then realizing the phenomenon of reducing the clamping stagnation when the first rolling element 13 moves along the first guide rail 11a, thereby improving the stability of the reciprocating body 12 driving the piston 102 to reciprocate, and avoiding the influence on the compression efficiency caused by the disturbance of the reciprocating rhythm of the piston 102.

The inventors found through studies that, when the value of R/L is in the range of 3 to 6, the reciprocating body 12 in the linear reciprocating mechanism 1002 can reach the most stable linear reciprocating state, and the movement rhythm of the piston 102 is the most stable.

As shown in fig. 7 and 8, the closed curve has peaks and valleys which are offset in the axial direction and the circumferential direction of the rotary transmission member 11. The peaks in the track of the first guide groove 11a and the peaks in the track of the second guide groove 11b are arranged offset in the circumferential direction of the rotary transmission member 11. Therefore, during the rotation of the rotary transmission member 11, the first rolling member 13 moving along the first guide groove 11a and the second rolling member 14 moving along the second guide groove 11b can respectively have a stable supporting effect at different positions on the circumferential side of the corresponding rotary transmission member 11, so that the movement of the reciprocating body 12 in the axial direction is more stable under the drive of the first rolling member 13 and the second rolling member 14.

In the embodiment provided with the first rolling member 13 and the second rolling member 14, when the rotary transmission member 11 rotates, the first rolling member 13 moves along the first guide groove 11a, and the second rolling member 14 moves along the second guide groove 11 b. The displacement variation of the first rolling element 13 and the second rolling element 14 in the axial direction of the rotary transmission element 11 is equal, so that the axial driving steps of the first rolling element 13 and the second rolling element 14 are coordinated and consistent, the probability of the rotary transmission element 11 being blocked is reduced, and the reciprocating motion reliability is improved.

In the linear reciprocating mechanism 1002, the reciprocating body 12 can reciprocate in the axial direction of the rotary transmission member 11 when the rotary transmission member 11 rotates, and therefore, the piston 102 can be reciprocated by the reciprocating body 12 by connecting the piston 102 to the reciprocating body 12.

As shown in fig. 8 and 9, the tracks of the first guide groove 11a and the second guide groove 11b are sinusoidal with the same amplitude, and this arrangement ensures that the first guide groove 11a and the second guide groove 11b respectively guide the periodicity of the movement of the first rolling member 13 and the second rolling member 14 to realize the reciprocating movement of the reciprocating body 12, and on the other hand, by this structural design, the tracks of the first rolling member 13 and the second rolling member 14 respectively roll along the first guide groove 11a and the second guide groove 11b are smoother, thereby avoiding the occurrence of the condition of bead jump or jamming and the like. Since the amplitudes of the sinusoidal curves corresponding to the tracks of the first guide groove 11a and the second guide groove 11b are the same, only the first rolling element 13 and the second rolling element 14 are correspondingly arranged at the peak position or the trough position of the first guide groove 11a and the second guide groove 11b, when the rotary transmission element 11 rotates, the displacement variation of the first rolling element 13 along the first guide groove 11a in the axial direction of the rotary transmission element 11 is consistent with the displacement variation of the second rolling element 14 along the second guide groove 11b in the axial direction of the rotary transmission element 11, and therefore, the arrangement of the structure is beneficial to determining the installation position of the first rolling element 13 and the second rolling element 14 relative to the rotary transmission element 11, so that the linear reciprocating mechanism 1002 is more convenient to assemble.

The number of peaks and valleys in the track of the first guide groove 11a and the second guide groove 11b is equal. Specifically, the number of peaks in the track of the first guide groove 11a is equal to the number of valleys in the track of the first guide groove 11a, the number of peaks in the track of the second guide groove 11b is equal to the number of valleys in the track of the second guide groove 11b, and the number of peaks in the track of the first guide rail is kept identical. In this embodiment, in the axial direction of the rotary transmission member 11, the peaks in the track of the first guide groove 11a are right opposite to the valleys in the track of the second guide groove 11 b. Thus, when the first rolling member 13 is located at the position of the trough of the first guide groove 11a, the second rolling member 14 is located at the position of the trough of the second guide groove 11b, and the first rolling member 13 and the second rolling member 14 are offset from each other in the circumferential direction of the rotary transmission member 11.

In the embodiment of the present application, the first rolling element 13 and the second rolling element 14 are offset from each other in the circumferential direction of the rotary transmission member 11, which means that the line connecting the first rolling element 13 and the second rolling element 14 is not parallel to the center line of the rotary transmission member 11, in other words, the positions of the first rolling element 13 and the second rolling element 14 in the circumferential direction of the rotary transmission member 11 are different.

In some embodiments, the number of first rolling elements 13 and second rolling elements 14 is 2, and the connecting lines of the 2 first rolling elements 13 and the connecting lines of the 2 second rolling elements 14 are perpendicular to the central line of the rotary transmission element 11. In this embodiment, the 2 first rolling members 13 and the 2 second rolling members 14 can realize the supporting and positioning between the reciprocating body 12 and the rotary transmission member 11 in two perpendicular directions perpendicular to the center line of the rotary transmission member 11, so that the reciprocating body 12 is driven by the rotary transmission member 11 to move smoothly along the axial direction and not easy to shake in the radial direction, and thus the reciprocating body 12 maintains good stability of movement along the axial direction of the rotary transmission member 11.

Referring again to fig. 6, the linear reciprocating mechanism 1002 further includes a base 10a, a housing 15, and a guide assembly 16. The case 15 is connected with the base 10a to enclose a movable space in which the rotary transmission member 11, the reciprocating body 12, and the guide assembly 16 are disposed. In this embodiment, the case 15 and the base 10a are connected to form a movable space, which can provide space for assembling and moving the rotary transmission member 11, the reciprocating body 12 and the guide assembly 16, thereby improving the assembling stability between these structures, and at the same time, the structural members in the movable space are not easy to enter dust due to the arrangement of the structure, so that the arrangement of the case 15 and the base 10a is advantageous for dust prevention of the linear reciprocating mechanism 1002. In some embodiments, sealing rings, and other structures may be disposed at corresponding positions of the case 15 and the base 10a to prevent water.

The rotation transmission member 11 is limited on the base 10a in the axial direction, that is, the rotation transmission member 11 does not move along the axial direction relative to the base 10a, so that when the rotation transmission member 11 rotates relative to the base 10a, rotation energy can be transmitted to the first rolling member 13 and the second rolling member 14 through the first guide groove 11a and the second guide groove 11b as much as possible, and displacement variation of the first rolling member 13 and the second rolling member 14 along the axial direction of the rotation transmission member 11 is maximized, which is further beneficial to maximization of reciprocating travel of the reciprocating body 12, so as to improve transmission efficiency of the linear reciprocating mechanism 1002.

In the above embodiment, when the rotary transmission member 11 rotates relative to the base 10a, the reciprocating body 12 is driven by the rotary transmission member 11 to reciprocate in the movable space along the guide assembly 16. The guide assembly 16 has a guide supporting effect on the reciprocating body 12, thereby further improving the stability of the linear reciprocating mechanism 1002.

With continued reference to fig. 6, the guide assembly 16 includes at least 2 guide rods 16a, and each guide rod 16a is connected at two ends to the base 10a and the case 15, respectively. In this embodiment, the guide rods 16a are parallel to the axial direction of the rotary actuator 11, and the reciprocating body 12 is slidably connected to the guide rods 16 a. Thus, when the rotary transmission member 11 rotates, the reciprocating body 12 slides smoothly along the guide rod 16 a. The reciprocating body 12 and the guide rod 16a can be slidably connected through the linear bearing 12c, so that the sliding friction force between the reciprocating body 12 and the guide rod 16a is reduced by using the linear bearing 12c, and the heat loss during the movement of the linear reciprocating mechanism 1002 is reduced, so that the energy conversion rate is improved. The reciprocating body 12 is a cavity with an inner cavity, the rotary transmission member 11 is positioned in the inner cavity, and the side wall of the reciprocating body 12 is provided with an installation space 121 penetrating to the inner cavity. The first and second mounting portions 12a and 12b each have the mounting space 121 so as to mount the first and second rolling members 13 and 14 into the corresponding mounting spaces 121 from the outside of the reciprocating body 12 such that the first and second rolling members 13 and 14 are fitted in the first and second guide grooves 11a and 11b, respectively.

As shown in fig. 6 and 7, in some embodiments, a plurality of balls 123 are respectively disposed in the mounting spaces 121 at the first mounting portion 12a and the second mounting portion 12b through ball sleeves 122, and the plurality of balls 123 disposed at the first mounting portion 12a are abutted against the first rolling member 13, so that the smoothness of movement of the first rolling member 13 along the first guide groove 11a is improved. Accordingly, the plurality of balls 123 provided in the second mounting portion 12b are abutted against the second rolling member 14, thereby improving the smoothness of movement of the second rolling member 14 along the second guide groove 11 b. A cover 124 is provided at the installation space 121. After the balls 123 are disposed in the corresponding installation spaces 121 by the ball covers 122, the notches of the installation spaces 121 may be covered by the cover 124 to limit the removal of the ball covers 122 from the installation spaces 121. Of course, in some embodiments, after the ball sleeve 122 is mounted to the mounting space 121, the ball sleeve 122 may be fastened to the reciprocating body 12 by clamping or welding.

The first rolling member 13 and the second rolling member 14 may be balls. It is understood that the diameter of the ball is larger than that of the ball 123, so that the plurality of balls 123 are abutted against the surface of the ball, and thus the ball 123 can reduce friction between the ball and the reciprocating body 12 and reduce jamming phenomenon when the ball rolls.

In the circumferential direction of the rotary transmission member 11, a guide bar 16a is provided between any adjacent first rolling member 13 and second rolling member 14. In this embodiment, the guide bar 16a is disposed in the space vacated by the staggered arrangement of the first rolling member 13 and the second rolling member 14 in the circumferential direction of the rotary transmission member 11, so that the linear reciprocating mechanism 1002 is not required to provide additional space, the space utilization of the movable space formed by the enclosure of the case 15 and the base 10a is improved, and the guide bar 16a can be used to support and guide the reciprocating body 12, so as to enhance the stability of the reciprocating motion of the reciprocating body 12 in the movable space.

In the embodiment in which the linear reciprocating mechanism 1002 is provided with 2 first rolling members 13 and 2 second rolling members 14, the 2 first rolling members 13 are provided 180 ° apart in the circumferential direction of the rotary transmission member 11, the 2 second rolling members 14 are provided 180 ° apart in the circumferential direction of the rotary transmission member 11, and any adjacent first rolling member 13 and second rolling member 14 are 90 ° apart in the circumferential direction of the rotary transmission member 11. At this time, the reciprocating body 12 receives a supporting force having 4 axial directions perpendicular to the rotary transmission member 11, and the supporting forces are uniformly arranged in the axial direction around the rotary transmission member 11, so that the reciprocating body 12 is stable in axial movement with respect to the rotary transmission member 11.

Further, the guide bar 16a is provided at an intermediate position in the circumferential direction of the adjacent first rolling member 13 and second rolling member 14 corresponding to the reciprocating body 12. That is, in the axial direction of the rotary transmission member 11, the guide bar 16a is disposed at 45 ° from the first rolling member 13, and the guide bar 16a is disposed at 45 ° from the second rolling member 14. In this way, the first rolling element 13, the second rolling element 14 and the guide rod 16a are arranged in the linear reciprocating mechanism 1002 in a rotationally symmetrical manner around the axial direction of the rotary transmission element 11, so that structural weights in all directions of the linear reciprocating mechanism 1002 are kept consistent, the phenomenon that the linear reciprocating mechanism 1002 is biased to one side during operation is reduced, and the overall stability of the linear reciprocating mechanism 1002 during operation is kept.

Referring again to fig. 1 and 2, in some embodiments, the base 10a is rotatably provided with a rotating member 17, the rotating member 17 is connected to the rotating transmission member 11, and the rotating member 17 is configured to rotate the rotating transmission member 11 relative to the base 10 a.

In this embodiment, since the rotating member 17 is rotatably connected with the base 10a, the rotation of the rotating member 11 is achieved, and only the connection between the rotating member 17 and the rotating member 11 is considered, so that the rotating member 11 can be individually processed, and the processing of the first guide groove 11a and the second guide groove 11b is facilitated. Accordingly, the rotational fitting process of the rotating member 17 with the base 10a does not need to take into consideration the structural shape of the rotary transmission member 11. During assembly, the rotary transmission member 11 and the rotary member 17 can be assembled step by step, so that the problem of inconvenience in assembly caused by the fact that the rotary member 17 and the rotary transmission member 11 are integrally assembled is avoided.

The rotating member 17 may be an output shaft of a motor, or may be an intermediate connecting member for linking with the output shaft of the motor, so long as the rotating member 17 can rotate relative to the base 10a to drive the rotation transmission member 11 to rotate.

With continued reference to fig. 1, in some embodiments, the base 10a is provided with first and second coaxially disposed planar bearings 14a, 14b, 14c, and 14d. The rotating member 17 includes a rotating disc 171 and a rotating shaft 172 coaxially connected, and the first flat bearing 14a and the second flat bearing 14b are interposed between the rotating disc 171 and the rotary transmission member 11 in the axial direction. The first rolling bearing 14c is sleeved between the peripheral side wall of the rotating disc 171 and the inner wall of the base 10a, and the second rolling bearing 14d is sleeved between the peripheral side wall of the rotating shaft 172 and the inner wall of the base 10 a.

As shown in fig. 1, the base 10a is provided with a through hole 141 for mounting the rotary member 17, the through hole 141 having a reduced section 141a, and both ends of the reduced section 141a are formed with a first stepped groove 141b and a second stepped groove 141c, respectively. The first plane bearing 14a is disposed in the first step groove 141b, one surface of the first plane bearing 14a is axially abutted against the rotating disc 171, and the other surface of the first plane bearing is kept in a gap with the rotating shaft 172, so that no rotational interference exists between the rotating shaft 172 and the base 10 a. The second planar bearing 14b is disposed in the second stepped groove 141c, and one surface of the second planar bearing 14b axially abuts against the rotary transmission member 11, and the other surface maintains a gap with the rotary shaft 172, so that there is no rotational interference between the rotary shaft 172 and the base 10 a.

In some embodiments, the end of the rotation transmission member 11 facing the rotation disc 171 is formed with a mounting hole 111 and a catching protrusion 112. One end of the rotating shaft 172 away from the rotating disc 171 is penetrated through the mounting hole 111, the clamping protrusion 112 is positioned at the periphery of the mounting hole 111, and the second rolling bearing 14d is sleeved between the outer peripheral wall of the clamping protrusion 112 and the inner wall of the base 10 a. In this embodiment, the second rolling bearing 14d may enable the rotation transmission member 11 to smoothly rotate with respect to the base 10 a. In this embodiment, the end surface of the click projection 112 abuts against the second flat bearing 14 b.

The rotating shaft 172 and the mounting hole 111 of the rotary transmission member 11 may be connected by clamping or welding, or may be locked by a nut after the rotating shaft 172 passes through the mounting hole 111. The connection between the rotation shaft 172 and the rotation transmission member 11 is not limited herein.

In some embodiments, compression cylinder 1001 further includes valve plate assembly 100.

As shown in connection with fig. 10, the valve plate assembly 100 includes a valve plate 1, a first valve plate 2, a pressure plate 3, and a second valve plate 4. The valve plate 1 is provided with a first mounting groove 1a, a second mounting groove 1b, a first air passage 1c and a second air passage 1d. The first air passage 1c penetrates to the bottom of the first installation groove 1a, and the second air passage 1d penetrates to the bottom of the second installation groove 1 b. The first valve plate 2 is arranged in the first mounting groove 1a, so that when the first valve plate 2 is attached to the first air passage 1c positioned at the bottom of the first mounting groove 1a, the first valve plate 2 can close the first air passage 1c; accordingly, when the first valve plate 2 is released from the attachment to the first air passage 1c, the first air passage 1c is not blocked by the first valve plate 2 and is in an open state. The pressing plate 3 is arranged in the second mounting groove 1b, and the pressing plate 3 is provided with a third air passage 3a. It will be appreciated that, if no other structure is provided between the pressure plate 3 and the valve plate 1, the pressure plate 3 provided in the second mounting groove 1b will communicate with the second air passage 1d at the bottom of the second mounting groove 1b because the third air passage 3a is exposed to the second mounting groove 1 b. The second valve plate 4 is clamped between the valve plate 1 and the pressing plate 3, so that the second valve plate 4 can close the third air passage 3a by attaching the third air passage 3a to block communication between the third air passage 3a and the second air passage 1 d; accordingly, when the second valve sheet 4 is released from the third air passage 3a, the third air passage 3a will be opened to communicate with the second air passage 1d. Thus, in the valve plate assembly 100 of the embodiment of the present application, the first valve sheet 2 may realize the closing and opening of the first air passage 1c, and the second valve sheet 4 may realize the closing and opening of the third air passage 3a.

It should be noted that, the first valve plate 2 and the second valve plate 4 are deformed in the air path due to airflow driving force to realize closing and opening of the corresponding channels, so that an opening and closing effect can be achieved without adopting an electric control. In this embodiment, the partial structure of the first valve plate 2 closes the first air passage 1c, and when the air flows from one side of the valve plate 1 facing away from the first valve plate 2 to the other side through the first air passage 1c, the portion of the first valve plate 2 corresponding to the first air passage 1c deforms to open the first air passage 1c. The third air passage 3a is closed by a part of the structure of the second valve plate 4, and when the air flows through the third air passage 3a towards the second air passage 1d, the part of the second valve plate 4 corresponding to the third air passage 3a deforms to open the third air passage 3a.

In the valve plate assembly 100 according to the embodiment of the present application, the first mounting groove 1a and the second mounting groove 1b on the valve plate 1 provide the mounting space for the first valve plate 2 and the second valve plate 4, respectively, so that the first valve plate 2 and the second valve plate 4 can be kept flat relative to the valve plate 1, and therefore, when the valve plate 1 is mounted on the cylinder 101 of the compression cylinder 1001, the mounting of the first valve plate 2 and the second valve plate 4 does not occupy the volume space in the cylinder 101, so that the piston 102 of the compression cylinder 1001 can fully utilize the volume space of the cylinder 101 to perform the reciprocating motion, so as to ensure the compression efficiency.

With continued reference to fig. 10, the first valve plate 2 and the second valve plate 4 each include an overlaying portion T and an elastic portion Q, where the elastic portion Q is used as a portion for generating deformation in the first valve plate 2 and the second valve plate 4, and a setting position of the elastic portion Q corresponds to an air passage to be closed. Both sides of the elastic part Q are separated from the attaching part T through the separation groove G, both ends of the elastic part Q are connected with the attaching part T, and the elastic part Q can elastically deform relative to the attaching part T under the thrust of air flow. Through this kind of structure setting, when taking place elastic deformation, elastic part Q's both ends can be pulled by the laminating portion T and can not appear by a wide margin motion to reduce elastic part Q and open the impact force that appears with the closure in-process to corresponding air flue, alleviateed the beat noise then.

At least one of the first air passage 1c, the second air passage 1d and the third air passage 3a is an arc-shaped groove. So that when the valve plate assembly 100 is assembled to the cylinder block 101 of the compression cylinder 1001, the circular arc-shaped groove may correspond to the cylindrical volume chamber 1011 of the cylinder block 101, so that a long and narrow communication area may be obtained to facilitate uniformity of flow of the air flow.

The elastic part Q is fan-shaped, so that when the elastic part Q is deformed due to the thrust of air flow, the fan-shaped elastic part Q is easy to stretch to leave the corresponding air passage and can turn over to a certain extent, and therefore the effect of the elastic part Q leaving the corresponding air passage to open the corresponding air passage can be optimized.

In some embodiments, the depth of the first mounting groove 1a is greater than or equal to the thickness of the first valve plate 2, so that after the first valve plate 2 is mounted in the first mounting groove 1a, the surface of the first valve plate 2 does not protrude from the surface of the valve plate 1 where the first mounting groove 1a is opened. In this way, after the valve plate assembly 100 is mounted to the block 101 of the compression cylinder 1001, the piston 102 can be moved to a position against the valve plate 1 without interference from the first valve plate 2, as permitted by the range of movement thereof. Here, the first valve plate 2 may be adhered to the valve plate 1 by glue, or may be connected to the valve plate 1 by thermo-compression molding, and the connection manner between the first valve plate 2 and the valve plate 1 is not limited herein.

With continued reference to fig. 10, the second installation groove 1b has a clearance groove 1e at the bottom thereof, and the second air passage 1d extends through to the bottom of the clearance groove 1 e. The position of the void-avoiding groove 1e in the second mounting groove 1b corresponds to a deformed portion of the second valve sheet 4. In this embodiment, the void space is provided for the deformation of the second valve plate 4 by using the void space 1e, so that the deformation amount of the second valve plate 4 is advantageously maintained, so as to improve the efficiency of opening the third air passage 3a by the second valve plate 4.

With continued reference to fig. 10, a first sealing ring 5 is disposed around the first valve plate 2, and the first sealing ring 5 is in sealing contact with the side wall of the first installation groove 1a, so that the air tightness between the periphery of the first valve plate 2 and the side wall of the first installation groove 1a is enhanced by using the first sealing ring 5, the air leakage probability is reduced, and the sealing effect of the first valve plate 2 when the first air passage 1c is closed is improved.

The second sealing ring 6 is arranged around the pressing plate 3 or the second valve plate 4, and the second sealing ring 6 is in sealing abutting connection with the side wall of the second installation groove 1b, so that the air tightness between the periphery of the pressing plate 3 or the second valve plate 4 and the side wall of the second installation groove 1b is enhanced by using the second sealing ring 6, the air leakage probability is reduced, and the sealing effect of the second valve plate 4 when the third air passage 3a is closed is improved.

Referring to fig. 3 and 4 again, when the piston 102 reciprocates in the volume chamber 1011, the first valve plate 2 and the second valve plate 4 are alternately deformed, so that the first air passage 1c and the third air passage 3a are alternately opened. In this embodiment, the first air passage 1c and the third air passage 3a are alternately opened by using the first valve plate 2 and the second valve plate 4, so that pumping and exhausting circulation in the air passage in the process of reciprocating the volume chamber 1011 of the piston 102 are realized, and the compression cylinder 1001 can pump and compress the air flow.

Here, the compression cylinder 1001 has air holes for intake air and for exhaust air. For ease of understanding, the working principle will be further described with reference to the structure of the compression cylinder 1001.

As further shown in connection with fig. 3 and 4, the compression cylinder 1001 further includes a first housing 104, and the first housing 104 is connected to one side of the cylinder block 101. The first housing 104 has a first air inlet 104a and a first air outlet 104b, and the valve plate assembly 100 is interposed between the cylinder block 101 and the first housing 104. In this embodiment, when the piston 102 moves in the first direction 1001a with respect to the cylinder 101, the first gas inlet 104a pumps gas into the volume chamber 1011 through the first gas passage 1c, and when the piston 102 moves in the second direction 1001b with respect to the cylinder 101, the piston 102 discharges the gas in the volume chamber 1011 from the first gas outlet 104b through the second gas passage 1d and the third gas passage 3a, and the first direction 1001a and the second direction 1001b are opposite directions. In this embodiment, the first air inlet 104a and the first air passage 1c constitute an air inlet passage for pumping air into the volume chamber 1011, and the second air passage 1d, the third air passage 3a, and the first air outlet 104b constitute an air outlet passage for discharging air from the volume chamber 1011. During the reciprocating motion of the piston 102, that is, when moving in the first direction 1001a and the second direction 1001b, the intake air path and the exhaust air path are alternately opened along with the piston 102 in one reciprocating cycle, so that it is ensured that gas does not leak from the exhaust air path when the volume chamber 1011 of the cylinder body 101 is intake, and gas does not leak from the intake air path when the volume chamber 1011 of the cylinder body 101 is exhaust from the exhaust air path, and therefore, the compression cylinder 1001 can periodically suck and exhaust during the continuous reciprocating motion of the piston 102 in a plurality of reciprocating cycles, thereby realizing the compression work.

The cylinder 101 is in sealing engagement with the valve plate 1, and the first housing 104 is in sealing engagement with the valve plate 1 and/or the cylinder 101. As shown in fig. 3 and 4, a first sealing member 105 is disposed between the cylinder 101 and the valve plate 1, a second sealing member 106 and a third sealing member 107 are disposed between the first housing 104 and the valve plate 1, wherein the second sealing member 106 is used for sealing between the first housing 104 and the valve plate 1 in an air inlet channel, and the third sealing member 107 is used for sealing between the first housing 104 and the valve plate 1 in an air outlet channel, that is, through the second sealing member 106 and the third sealing member 107, airtight blocking between the air inlet channel and the air outlet channel can be realized, so that in the process of air suction link and air outlet link, the air inlet channel and the air outlet channel do not interfere with each other when the compression cylinder 1001 works. The first seal 105 may be an O-ring interposed between the cylinder 101 and the valve plate 1.

As shown in connection with fig. 11, in some embodiments, the first housing 104 is formed with an intake chamber 104c and an exhaust chamber 104d. The first air inlet 104a communicates with the air inlet chamber 104c, and the first air outlet 104b communicates with the air outlet chamber 104d. The intake chamber 104c and the exhaust chamber 104d may be formed separately from a partition 104e in the first housing 104. When the valve plate 1 is fitted with the first housing 104, the valve plate 1 covers the end face of the first housing 104 on the side where the intake chamber 104c and the exhaust chamber 104d are formed, and the second seal 106 and the third seal 107 between the valve plate 1 and the first housing 104 correspond to the intake chamber 104c and the exhaust chamber 104d, respectively, so that the intake chamber 104c and the exhaust chamber 104d do not communicate with each other between the valve plate 1 and the first housing 104.

The second seal 106 and the third seal 107 may be an integrally formed structure, so that the assembly step may be simplified.

The shape of the first sealing member 105 may be triangular, fan-shaped or circular, and the shape of the second sealing member 106 may be triangular, fan-shaped or circular. When the shapes of the first sealing member 105 and the second sealing member 106 are fan-shaped, the processing of the first housing 104 is simplified and the structural strength of the first housing 104 is maintained. For example, the side of the first housing 104 facing the valve plate 1 is provided in a circular shape, wherein the shapes of the intake chamber 104c and the exhaust chamber 104d on the end surfaces of the corresponding first housing 104 are in a fan shape.

The shapes of the second seal 106 and the third seal 107 may be set to other shapes according to the shape design requirements, and are not limited herein.

As shown in connection with fig. 12 to 14, in another embodiment, the compression cylinder 1001 includes a first housing 104 and a second housing 108. The first housing 104 and the second housing 108 are connected to both sides of the cylinder 101, respectively. The piston 102 divides the volume 1011 into a first volume 1011a and a second volume 1011b, the first volume 1011a being located between the first housing 104 and the piston 102, and the second volume 1011b being located between the second housing 108 and the piston 102.

In this embodiment, as shown in conjunction with fig. 14, the first housing 104 has a first air inlet 104a and a first air outlet 104b, the second housing 108 has a second air inlet 108a and a second air outlet 108b, and the compression cylinder 1001 includes 2 sets of valve plate assemblies 100, and it is understood that the 2 sets of valve plate assemblies 100 have the same structure.

For convenience of description, the 2 sets of valve plate assemblies 100 will be referred to as "first valve plate assembly 100a" and "second valve plate assembly 100b", respectively.

The first valve plate assembly 100 is sandwiched between the cylinder block 101 and the first housing 104, and the second valve plate assembly 100 is sandwiched between the cylinder block 101 and the second housing 108.

When the piston 102 moves in the first direction 1001a relative to the cylinder 101, the first gas inlet 104a pumps gas into the first chamber 1011a through the first gas passage 1c of the first valve plate assembly 100a, and the piston 102 discharges the gas in the second chamber 1011b from the second gas outlet 108b through the second gas passage 1d and the third gas passage 3a of the second valve plate assembly 100 b.

When the piston 102 moves in the second direction 1001b relative to the cylinder 101, the second air inlet 108a pumps air into the second cavity 1011b through the first air passage 1c of the second valve plate assembly 100b, and the piston 102 discharges air in the first cavity 1011a from the first air outlet 104b through the second air passage 1d and the third air passage 3a of the first valve plate assembly 100a, and the first direction 1001a is opposite to the second direction 1001 b.

With this arrangement, compression work can be performed regardless of whether the piston 102 moves in the first direction 1001a or in the second direction 1001b, thereby effectively improving compression efficiency.

It should be noted that the first housing 104 and the second housing 108 have substantially the same structure, and the structure of the second housing 108 is not described herein.

In some embodiments, the piston 102 is connected to the piston rod 103 and is connected to the linear reciprocating mechanism 1002 through the piston rod 103, and the linear reciprocating mechanism 1002 drives the piston rod 103 to make telescopic motion relative to the cylinder 101, so that the piston 102 makes reciprocating motion in the volume 1011 of the cylinder 101 under the driving of the piston rod 103.

Further, as shown in fig. 1 and 2, the piston 102 is connected to the reciprocating body 12 via a piston rod 103. Specifically, one end of the piston rod 103 is connected to the reciprocating body 12, and the other end of the piston rod 103 is connected to the piston 102. The piston rod 103 and the reciprocating body 12 can be in threaded connection, hot melt connection or snap connection, or the piston rod 103 and the reciprocating body 12 are connected through bolts. The piston 102 may be screwed to the piston rod 103 or may be engaged with the piston rod 103. The connection between the piston rod 103 and the piston 102 and the connection between the piston rod 103 and the reciprocating body 12 are not limited herein.

The piston rod 103 may exert a force transfer effect between the reciprocating body 12 and the piston 102. When the rotary transmission member 11 rotates, the reciprocating body 12 reciprocates in the housing 15 in the axial direction of the rotary transmission member 11, so that the piston rod 103 is telescopically moved relative to the housing 15, and thus the piston 102 connected to the piston rod 103 can reciprocate in the cylinder 101.

It should be noted that, the housing (e.g., the first housing 104) of the compression cylinder 1001 may be connected to the case 15, so as to implement the assembly between the compression cylinder 1001 and the linear reciprocating mechanism 1002. In some embodiments, the first housing 104 of the compression cylinder 1001 may be connected to the case 15 by a snap fit connection or by a bolt, and the specific connection manner is not limited herein.

In some embodiments, the first housing 104 is in sealing engagement with the case 15, and the sealing structure such as the bush 18 or the gurley 19 may be disposed on a structural portion of the first housing 104 and the case 15 near the piston rod 103, so long as the position where the piston rod 103 is inserted can be sealed. For example, the housing 15 is provided with a shaft hole 15a through which the piston rod 103 extends, and a bush 18 is interposed between the inner wall of the shaft hole 15a and the outer wall of the piston rod 103. The bush 18 seals the gap between the inner wall of the shaft hole 15a and the outer wall of the piston rod 103, thereby achieving waterproof and dustproof effects. The bushing 18 may be made of a wear-resistant material such as plastic or rubber. In some embodiments, a gurley 19 may be further disposed in the shaft hole 15a, where the gurley 19 is sleeved on the piston rod 103, so as to further enhance the sealing effect by using the gurley 19. The gurley 19 has low friction, no creeping, small starting force and high pressure resistance, so that the sealing between the piston rod 103 and the shaft hole 15a by utilizing the gurley 19 can not prevent the piston rod 103 from smoothly stretching and retracting relative to the box body 15 under the driving of the reciprocating body 12.

The compression cylinder 1001 is provided with a hole through which the piston rod 103 penetrates the volume 1011, so that the piston rod 103 can be connected to the piston 102 located in the volume 1011. For example, when the piston rod 103 is connected to the side of the piston 102 facing the valve plate assembly 100, the valve plate 1 in the valve plate assembly 100 is provided with perforations. In the embodiment in which the two sides of the cylinder body 101 are provided with the valve plate assemblies 100, only the valve plate 1 of the valve plate assembly 100, through which the piston rod 103 needs to be penetrated, needs to be perforated, and the valve plate assembly 100 on the other side does not need to meet the penetrating requirement of the valve plate assembly 100, so that perforation is not required to be arranged.

Taking the example that the piston rod 103 penetrates through the first housing 104 and the valve plate 1 of the first valve plate assembly 100a, perforations are formed in positions corresponding to the positions of the first housing 104 and the valve plate 1 of the first valve plate assembly 100a, so that one end of the piston rod 103 penetrates into the volume chamber 1011 from the perforations, and one end of the piston rod 103 can be connected with the piston 102 located in the volume chamber 1011. The connection between the piston rod 103 and the piston 102 includes, but is not limited to, a snap fit or a threaded connection.

With continued reference to fig. 14, the piston rod 103 may be sealed by a sealing structure such as a bushing 18 or a gurley 19 at a position penetrating the valve plate 1 and the first housing 104, so that the volume chamber 1011 has good air tightness.

Radiating fins 1012 can be arranged on the periphery of the cylinder body 101, so that heat generated when the piston 102 moves in the volume cavity 1011 of the cylinder body 101 can be dissipated in time, and damage caused by overhigh temperature of the compression cylinder 1001 is avoided.

The technical features of the above-described embodiments may be arbitrarily combined, and all possible combinations of the technical features in the above-described embodiments are not described for brevity of description, however, as long as there is no contradiction between the combinations of the technical features, they should be considered as the scope of the description.

The above examples illustrate only a few embodiments of the application, which are described in detail and are not to be construed as limiting the scope of the claims. It should be noted that it will be apparent to those skilled in the art that several variations and modifications can be made without departing from the inventive concept of the present application, which fall within the scope of the application. Accordingly, the scope of protection of the present application is to be determined by the appended claims.

Claims (10)

1.A linear reciprocating mechanism, comprising:

the device comprises a rotary transmission part, wherein a first guide groove is formed in the circumferential surface of the rotary transmission part, the track of the first guide groove is a closed curve encircling the rotary transmission part for a circle, and the closed curve is a sine curve;

a reciprocating body provided with a first mounting portion;

The first rolling piece is arranged on the first mounting part and matched with the first guide groove;

when the rotary transmission member rotates, the first rolling member moves along the first guide groove to drive the reciprocating body to reciprocate along the axial direction of the rotary transmission member, the reciprocating motion stroke of the reciprocating body is L, the distance from the center of the first rolling member to the center line of the rotary transmission member is R, and the value range of R/L is 1-8.

2. The linear reciprocating mechanism according to claim 1, wherein the circumferential surface of the rotary transmission member is provided with a second guide groove, tracks of the first guide groove and the second guide groove are sinusoidal curves with the same amplitude, the first guide groove and the second guide groove are arranged at intervals along the axial direction of the rotary transmission member, peaks in the track of the first guide groove and peaks in the track of the second guide groove are arranged in a staggered manner in the circumferential direction of the rotary transmission member, the reciprocating body is provided with a second mounting portion which is relatively fixed with the first mounting portion, the second mounting portion is used for mounting a second rolling member, the second rolling member is matched with the second guide groove, when the rotary transmission member rotates, the first rolling member moves along the first guide groove, the second rolling member moves along the second guide groove, and displacement variation amounts of the first rolling member and the second rolling member in the axial direction of the rotary transmission member are equal.

3. The linear reciprocating mechanism of claim 2, wherein the number of said first rolling elements and said second rolling elements is 2, and the line connecting 2 of said first rolling elements and the line connecting 2 of said second rolling elements are each perpendicular to the center line of said rotary transmission member.

4. The linear reciprocating mechanism of claim 3, further comprising a base, a box and a guide assembly, wherein the box is connected with the base to enclose a movable space, the rotary transmission member, the reciprocating body and the guide assembly are all disposed in the movable space, the rotary transmission member is axially limited to the base, and the reciprocating body reciprocates in the movable space along the guide assembly under the drive of the rotary transmission member when the rotary transmission member rotates relative to the base.

5. The linear reciprocating mechanism of claim 4, wherein the base is rotatably provided with a rotating member, the rotating member is connected to the rotary transmission member, and the rotating member is configured to drive the rotary transmission member to rotate relative to the base.

6. A compression device, comprising a compression cylinder and a linear reciprocating mechanism according to any one of claims 1-5, wherein the compression cylinder comprises a cylinder body and a piston, the cylinder body is provided with a volume cavity, the piston is arranged in the volume cavity, the piston is connected with the reciprocating body, and when the rotary transmission member rotates, the piston is driven by the reciprocating body to reciprocate.

7. The compression device of claim 6, wherein the compression device comprises a first housing and a first valve plate assembly, the first housing having a first air inlet and a first air outlet, the first valve plate assembly being sandwiched between the cylinder and the first housing, the first valve plate assembly comprising a valve plate, a first valve plate, a pressure plate, and a second valve plate, the valve plate having a first mounting groove, a second mounting groove, a first air passage, and a second air passage, the first air passage extending through the bottom of the first mounting groove, the second air passage extending through the bottom of the second mounting groove, the first valve plate being disposed in the first mounting groove, a portion of the first valve plate closing the first air passage, the pressure plate being disposed in the second mounting groove, the pressure plate having a third air passage, the second valve plate being sandwiched between the valve plate and the pressure plate, a portion of the second valve plate closing the third air passage, the first air passage moving in a first direction relative to the cylinder, the first air passage moving in a second direction from the first air passage through the first air passage to the first air passage, and the first air passage moving in a volume opposite the first direction from the first air passage to the first air passage, and the second air passage, and the volume.

8. The compression device of claim 7, wherein the first valve plate and the second valve plate each comprise a covering portion and an elastic portion, both sides of the elastic portion are respectively disposed on the covering portion through separation grooves, both ends of the elastic portion are respectively connected to the covering portion, and the elastic portion can elastically deform relative to the covering portion under thrust of air flow.

9. The compression device of claim 7, wherein the cylinder is in sealing engagement with the valve plate and the first housing is in sealing engagement with the valve plate and/or the cylinder.

10. The compression device of claim 7, further comprising a second housing, the first housing and the second housing being connected to respective sides of the cylinder, the piston dividing the volume into a first volume and a second volume, the first volume being located between the first housing and the piston, the second volume being located between the second housing and the piston, the second housing having a second air inlet and a second air outlet, the compression cylinder comprising a second valve plate assembly, the second valve plate assembly being identical in structure to the first valve plate assembly, the second valve plate assembly being sandwiched between the cylinder and the second housing; when the piston moves towards a first direction relative to the cylinder body, the first air inlet pumps air into the first containing cavity through the first air passage of the first valve plate assembly, and the piston discharges the air in the second containing cavity from the second air outlet through the second air passage and the third air passage of the second valve plate assembly; when the piston moves towards the second direction relative to the cylinder body, the second air inlet pumps air into the second containing cavity through the first air passage of the second valve plate assembly, and the piston discharges the air in the first containing cavity from the first air outlet through the second air passage and the third air passage of the first valve plate assembly.