阅读说明：本技术 一种凸轮式往复压缩机构 (Cam type reciprocating compressor mechanism ) 是由 耿茂飞 王乐 邢志胜 毛京兵 张成彦 于 2020-05-12 设计创作，主要内容包括：本发明属于压缩机技术领域,具体涉及一种凸轮式往复压缩机构,包括由气缸、活塞、活塞杆组成的活塞组件,所述活塞杆连接在气缸内的活塞上并沿气缸的长度方向做往复运动,该机构还包括转动盘,所述转动盘的板面内设有轮廓为凸轮状的环形轨道槽,活塞杆的外端部连接至轨道槽中,当转动盘在动力源的驱动下转动时,活塞杆的外端部与轨道槽之间构成相对滑动或滚动,活塞杆推动活塞在气缸内做往复运动,避免了旋转惯性力的产生,使压缩机工作时更加平稳。(The invention belongs to the technical field of compressors, and particularly relates to a cam type reciprocating compression mechanism which comprises a piston assembly consisting of a cylinder, a piston and a piston rod, wherein the piston rod is connected to the piston in the cylinder and reciprocates along the length direction of the cylinder.)

1. The utility model provides a cam type reciprocating compression mechanism, includes the piston assembly who comprises cylinder (10), piston (11), piston rod (12) are connected on piston (11) in cylinder (10) and are reciprocating motion along the length direction of cylinder (10), its characterized in that: the mechanism further comprises a rotating disc (20), an annular track groove (21) with a cam-shaped outline is formed in the plate surface of the rotating disc (20), the outer end of the piston rod (12) is connected into the track groove (21), when the rotating disc (20) rotates under the driving of a power source, relative sliding or rolling is formed between the outer end of the piston rod (12) and the track groove (21), and the piston rod (12) pushes the piston (11) to reciprocate in the cylinder (10).

2. The cam-type reciprocating compression mechanism of claim 1, wherein: the number of the cams forming the track of the track groove (21) is multiple, each cam is in central symmetry with respect to the central point of the rotating disc (20), and two adjacent cams in the track groove (21) are in curve smooth transition.

3. A cam-type reciprocating compression mechanism according to claim 1 or 2, wherein: the piston assemblies are arranged in a plurality of groups in pairs along the circumferential direction of the track groove (21), and the piston assemblies in each pair are distributed at equal intervals.

4. A cam-type reciprocating compression mechanism according to claim 1 or 2, wherein: the edge profile of the rotating disc (20) is consistent with the track of the track groove (21), and the center position of the rotating disc is connected with the driving shaft (30).

5. The cam-type reciprocating compression mechanism of claim 1, wherein: an outer line (211) of the track groove (21) is determined according to the following formula:

wherein rho is the distance between any point on the outer line of the track groove (21) and the center of the cam,d is the diameter of the outer circle of the cam, D is the diameter of the inner circle of the cam, N is the number of the cams, X is the X coordinate of any point on the outer line of the track groove (21), and Y is the Y coordinate of any point on the outer line of the track groove (21).

6. The cam-type reciprocating compression mechanism of claim 5, wherein: the distance between the inner line (212) and the outer line (211) of the track groove (21) is matched with the size of the outer end part of the piston rod (12) connected in the track groove (21).

7. The cam-type reciprocating compression mechanism of claim 6, wherein: the outer end part of the piston rod (12) is connected into the track groove (21) through a sliding block (121), and the sliding block (121) and the track groove (21) form relative sliding or rolling.

8. The cam-type reciprocating compression mechanism of claim 6, wherein: the piston rod (12) is sleeved with a guide ring (40), a through hole in the guide ring (40) is the same as the diameter of the piston rod (12), and the guide ring (40) and the cylinder (10) are kept in a relative static state.

9. The cam-type reciprocating compression mechanism of claim 1, wherein: the notch of the track groove (21) is in a closed-up shape and points to the piston assembly.

Technical Field

The invention belongs to the technical field of compressors, and particularly relates to a cam type reciprocating compression mechanism.

Background

The piston compressor is widely applied to petrochemical industry, natural gas, transportation, medical treatment, textile and food industry, and has an important position in the development of national economy and the improvement of social living standard. Traditional piston compressor passes through crank link mechanism, converts the rotary motion of bent axle into the reciprocating motion of piston, and mechanisms such as crank pin, crank are at rotatory in-process, and unbalanced rotating mass can arouse rotatory inertial force, and the rotational speed is higher, and rotatory inertial force is big more, and the vibration is big more, and through the balanced eccentric mass of balancing piece, will increase system energy consumption, reduce efficiency.

Disclosure of Invention

The invention aims to provide a cam type reciprocating compression mechanism, which avoids the generation of rotating inertia force and enables the compressor to work more stably.

In order to achieve the purpose, the invention adopts the following technical scheme: a cam type reciprocating compression mechanism comprises a piston assembly consisting of a cylinder, a piston and a piston rod, wherein the piston rod is connected to the piston in the cylinder and reciprocates along the length direction of the cylinder, the cam type reciprocating compression mechanism further comprises a rotating disc, an annular track groove with a cam-shaped outline is arranged in the plate surface of the rotating disc, the outer end part of the piston rod is connected into the track groove, when the rotating disc rotates under the driving of a power source, relative sliding or rolling is formed between the outer end part of the piston rod and the track groove, and the piston rod pushes the piston to reciprocate in the cylinder.

Preferably, the number of the cams constituting the track of the track groove is plural, and each cam is centrosymmetric with respect to the center point of the rotating disc, and the two adjacent cams in the track groove are smoothly transited in a curve.

Preferably, the piston assemblies are arranged in pairs along the circumferential direction of the track groove, and the piston assemblies in each pair are distributed at equal intervals.

Preferably, the edge profile of the rotating disk is consistent with the track of the track groove, and the central point of the rotating disk is connected with the driving shaft.

Preferably, the outer line of the track groove is determined according to the following formula:

wherein rho is any one of the outer lines of the track groovesThe distance between the point and the center of the cam,d is the diameter of the outer circle of the cam, D is the diameter of the inner circle of the cam, N is the number of the cams, X is the X coordinate of any point on the outer line of the track groove, and Y is the Y coordinate of any point on the outer line of the track groove.

Preferably, the distance between the inner line and the outer line of the track groove is matched with the size of the outer end part of the piston rod connected in the track groove.

Preferably, the outer end of the piston rod is connected to the track groove through a sliding block, and the sliding block and the track groove form relative sliding or rolling.

Preferably, the piston rod is sleeved with a guide ring, a through hole in the guide ring has the same diameter as the piston rod, and the guide ring and the cylinder are kept in a relatively static state.

Preferably, the notch of the track groove is in a closed shape, and the notch points to the piston assembly.

The invention has the beneficial effects that:

1) when the outer end part of the piston rod moves to the far point of the track groove, the piston rod drives the piston to be in the maximum contraction state; when the outer end part of the piston rod moves to the near point of the track groove, the piston rod drives the piston to be in the maximum extending state, the piston rod drives the piston to reciprocate in the cylinder, the gas in the cylinder is compressed, the mechanism is connected into the compressor, a crank connecting rod structure of a traditional piston compressor is replaced, the rotating inertia force of a crank and a crank pin is eliminated, the vibration of the compressor is reduced, the compressor works more stably, the compressor can run at a higher rotating speed, and the efficiency is improved;

2) the number of the cams in the track groove is multiple, the track groove rotates along with the rotating disc for a circle, the cylinder can completely perform a plurality of reciprocating motions, the air quantity of the compressor is increased, and the compressor is more efficient. The number of the cams of the track groove is flexibly adjusted according to the compression stage number and the air quantity, so that the compressor has strong applicability;

3) the two piston assemblies symmetrically arranged in pairs can effectively counteract the acting force generated by the piston rod on the groove wall of the track groove in the reciprocating motion process, so that the device is more stable in operation;

4) the edge profile of the rotating disc is consistent with the track of the track groove, so that the structure of the mechanism is more compact, and the rotating surface generated by the rotating disc during rotation is minimized;

5) when the outer end part of the piston rod slides in the track groove, the outer end part of the piston rod is tightly attached to the inner line and the outer line of the track groove, no shaking is caused, and the structure is stable;

6) the arrangement of the guide ring further ensures that when the piston rod reciprocates, the rod core of the piston rod is consistent with the axis of the cylinder, and the eccentric phenomenon is avoided.

Drawings

FIG. 1 is a schematic structural view of the present invention;

FIG. 2 is a schematic cross-sectional view along the plate surface of a rotating disk;

FIG. 3 is a groove pattern diagram of a three-cam track groove;

FIG. 4 is a groove pattern diagram of two cam track grooves;

fig. 5 is a groove pattern diagram of four cam track grooves.

Detailed Description

For the purpose of facilitating understanding, the present invention will be described in detail below with reference to the accompanying drawings.

A cam type reciprocating compression mechanism comprises a piston assembly consisting of a cylinder 10, a piston 11 and a piston rod 12, wherein the piston rod 12 is connected to the piston 11 in the cylinder 10 and reciprocates along the length direction of the cylinder 10, the mechanism further comprises a rotating disc 20, an annular track groove 21 with a cam-shaped outline is arranged in the plate surface of the rotating disc 20, the outer end of the piston rod 12 is connected into the track groove 21, when the rotating disc 20 rotates under the driving of a power source, relative sliding or rolling is formed between the outer end of the piston rod 12 and the track groove 21, and the piston rod 12 pushes the piston 11 to reciprocate in the cylinder 10. The outer end of the piston rod 12 is connected to the track groove 21, when the rotating disc 20 is driven by the power source to rotate, the outer end of the piston rod 12 and the cam-shaped profile of the annular track groove 21 form relative sliding or rolling, wherein the centers of the cylinder 10, the piston 11, the piston rod 12 and the rotating disc 20 are positioned on the same straight line, and when the outer end of the piston rod 12 moves to a far point of the track groove 21, the piston rod 12 drives the piston 11 to be in a maximum contraction state; when the outer tip of piston rod 12 moved the near point of track groove 21, piston rod 12 drove piston 11 and is in the biggest state of stretching out, track groove 21 promotes piston rod 12 and moves along pointing to and keeping away from the central point direction promptly, piston rod 12 drove piston 11 and is reciprocating motion in cylinder 10, realize the compression to the jar internal gas, be connected to this mechanism in the compressor, replace traditional piston compressor's crank connecting rod structure, the rotatory inertia force of crank and crank pin has been eliminated, the vibration of compressor has been reduced, compressor during operation is more steady, make the compressor can operate under higher rotational speed, and the efficiency is improved.

The number of the cams forming the track of the track groove 21 is plural, each cam is centrosymmetric with respect to the center point of the rotating disc 20, and the two adjacent cams in the track groove 21 are smoothly transited in a curve. A plurality of cams are arranged in the track of the track groove 21, when the rotating disc 20 rotates, relative sliding or rolling is formed between the outer end part of the piston rod 12 and the track groove 21, the plurality of cams drive the piston rod 12 in sequence, the inflection point between the cams is the near point of the track groove 21, at the moment, the piston rod 12 is in the maximum extending state at the position, and the piston rod 12 is in the maximum retracting state at the far point of the cams. The number of the cams of the track groove 21 is N, and the track groove 21 rotates one circle along with the rotating disc 20, so that the cylinder can completely perform N reciprocating motions, the air volume of the compressor is increased, and the compressor is more efficient. The number of cams in the track groove 21 is flexibly adjusted according to the number of compression stages and the amount of air, so that the compressor has strong applicability.

The piston assemblies are arranged in pairs along the circumference of the track groove 21, and the piston assemblies in each pair are distributed at equal intervals. When the track groove 21 rotates along with the rotating disc 20, the two piston assemblies which are symmetrically arranged in pairs can effectively counteract the acting force generated by the piston rod 12 on the groove wall of the track groove 21 in the reciprocating motion process, so that the device is more stable in operation, and in addition, the number of cams and the number of piston assemblies in the track groove 21 can be flexibly adjusted according to the compression stage number and the air quantity, so that the compressor has strong applicability.

The edge of the rotary disk 20 is contoured to coincide with the track of the track groove 21, and the center point thereof is connected to the driving shaft 30. In order to make the structure of the mechanism more compact, the rotating surface generated when the rotating disc 20 rotates is minimized, the edge contour of the rotating disc 20 is consistent with the track of the track groove 21, namely, the edge contour of the rotating disc 20 is cam-shaped, so that the design of the compressor is more miniaturized, and the central point position is connected with the driving shaft 30 for providing power.

As shown in fig. 3, the outer line 211 of the track groove 21 is determined according to the following formula:

wherein ρ is the distance between any point on the outer line of the track groove 21 and the center of the cam,d is the diameter of the outer circle of the cam, D is the diameter of the inner circle of the cam, N is the number of cams, X is the X coordinate of any point on the outer line of the track groove 21, Y is the Y coordinate of any point on the outer line of the track groove 21, and the intersection point of the X coordinate and the Y coordinate is located at the central point of the track groove 21.

The distance between the inner line 212 and the outer line 211 of the track groove 21 is matched with the size of the outer end part of the piston rod 12 connected in the track groove 21, namely, when the outer end part of the piston rod 12 slides in the track groove 21, the outer end part of the piston rod is tightly attached to the inner line 212 and the outer line 211 of the track groove 21, no shaking exists, and the structure is stable.

The outer end of the piston rod 12 is connected to the track groove 21 via a sliding block 121, and the sliding block 121 and the track groove 21 form relative sliding or rolling.

The piston rod 12 is sleeved with a guide ring 40, a through hole on the guide ring 40 has the same diameter as the piston rod 12, and the guide ring 40 and the cylinder 10 keep a relative static state. The arrangement of the guide ring 40 further ensures that when the piston rod 12 reciprocates, the rod core of the piston rod 12 is consistent with the axis of the cylinder 10, and no eccentricity occurs.

The notch of the track groove 21 is closed and points to the piston assembly.