CN210599821U

CN210599821U - Balanced crankshaft and corresponding reciprocating compressor

Info

Publication number: CN210599821U
Application number: CN201921064534.5U
Authority: CN
Inventors: 蒋兴华; 金晶; 黄燕; 邓元红
Original assignee: Shanghai Orient Compressor Manufacturing Co ltd
Current assignee: Shanghai Orient Compressor Manufacturing Co ltd
Priority date: 2019-07-09
Filing date: 2019-07-09
Publication date: 2020-05-22
Anticipated expiration: 2029-07-09

Abstract

The utility model relates to a balanced type bent axle and corresponding reciprocating compressor, wherein, the action point both sides of balanced type bent axle be equipped with a balancing piece respectively, can effectively reduce the volume of balancing piece quality and crankcase, because the balancing piece external diameter reduces, has effectively reduced the height of crankcase, through calculating, the moment that the compressor produced in rotatory a week is effectual is offset completely by the balancing piece. The balanced crankshaft and the corresponding reciprocating compressor adopting the structure can reasonably reduce the investment cost while ensuring the performance.

Description

Balanced crankshaft and corresponding reciprocating compressor

Technical Field

The utility model relates to the field of machinary, especially, relate to bent axle technical field, specifically indicate a balanced type bent axle and corresponding reciprocating compressor.

Background

In the prior art, the advantages that the volume of a unit and the floor area of a factory building can be greatly reduced by a high-speed compressor compared with a low-speed compressor are widely applied, so that the compressor with high speed and low speed and vibrating is obvious and large for a long time, and is always used as a research object for a long time. The main reason is that the reciprocating inertia force and moment can not be effectively balanced, and the unbalanced inertia force and moment are in direct proportion to the square of the rotating speed of the compressor, so the rotating speed is higher, and the vibration value is larger. Although the prior art also applies the balance weight to the crankshaft to solve the problem, the prior art has a balance weight at the middle position of the crankshaft, the acting force distance is short, so that the balance mass needs to be large, the volume requirement of the crankcase is also large, the structure of the crankcase can be seen as shown in fig. 1, the directions indicated by arrows in the figure are all reciprocating inertia forces acting on the crankshaft, the balance weight 1 can be seen from the figure to be arranged at the middle position of the crankshaft and positioned at the same side of the disturbance moment acting point 2, the volume of the balance weight 1 arranged at the position is large, and therefore, the requirement on the volume of the crankcase is also large. It is necessary to add a counterweight to the crank arm in order to balance the reciprocating inertia moment of the compressor, so that the moment generated by the train is cancelled, but since the mass demand of this form for the counterweight is greater, it is necessary to balance the whole train of reciprocating inertia masses.

SUMMERY OF THE UTILITY MODEL

The utility model aims at overcoming the shortcoming of above-mentioned prior art, providing a balanced type bent axle and corresponding reciprocating compressor that can reduce balancing piece quality and crankcase body.

In order to achieve the above object, the present invention provides a balanced type crankshaft and corresponding reciprocating compressor, comprising:

the balanced crankshaft is mainly characterized in that two sides of a disturbance torque action point of the balanced crankshaft are respectively provided with a balanced block.

Preferably, the two balance weights have equal mass, opposite radial directions of the axes and opposite mass centers.

Preferably, the axis of one balance weight and the axis of one crank throw in the balanced crankshaft form an included angle of 45 degrees, and the axis of the other balance weight and the axis of the crank throw form an included angle of-45 degrees.

The reciprocating compressor comprises a cylinder body and a balanced crankshaft arranged in the cylinder body, and is mainly characterized in that the balanced crankshaft is any one of the balanced crankshafts.

By adopting the balanced crankshaft and the corresponding reciprocating compressor, because two sides of the action point of the balanced crankshaft are respectively provided with a balance block, the mass of the balance block and the volume of a crankcase can be effectively reduced, and because the outer diameter of the balance block is reduced, the height of the crankcase is effectively reduced.

Drawings

Fig. 1 is a schematic diagram of a crankshaft in the prior art.

Fig. 2 is a front view of the balanced crankshaft of the present invention.

Fig. 3 is a side view of the balanced crankshaft of the present invention.

FIG. 4 is a schematic diagram of the relationship between the torque and the mass torque.

Reference numerals

1 balance weight

2 disturbance moment acting point

3 first crank throw

4 second crank throw

5 third crank throw

6 fourth crank throw

Detailed Description

In order to more clearly describe the technical content of the present invention, the following further description is given with reference to specific embodiments.

In this embodiment, the present invention is explained by taking the four-row reciprocating compressor as the original form, and as shown in fig. 2 and 3, the balance crankshaft in this embodiment eliminates the balance weight 1 on the crank arm of the crankshaft in the prior art, and a balance weight 1 is respectively provided on both sides of the disturbance moment acting point 2. The two balance weights 1 have equal mass, opposite axial radial directions and opposite mass center directions.

In this embodiment, the axis of one of the balance weights 1 forms an angle of 45 ° with the axis of one of the cranks in the balanced crankshaft, and the axis of the other balance weight 1 forms an angle of-45 ° with the axis of the crank.

This arrangement reduces the number of counterweights 1 on the crankshaft from 4 to 2 in the prior art, reducing the mass by 50%. The moment generated by the compressor in one rotation is effectively and completely offset by the balance block 1 through calculation.

In the above embodiment, the balance weight 1 is added at the two ends of the crankshaft and forms-45 degrees (-45 degrees) with the axis of the crank throw, so that the distance between the balance weight 1 and the disturbing moment action point 2 of the compressor is increased, and the mass of the balance weight 1 required for balancing the reciprocating moment is reduced. The force component of the balance weight 1 with the angle of 45 degrees in the horizontal direction ensures the balance of moment which is always kept in the rotation process of the compressor, thereby eliminating the vibration of the compressor.

As shown in fig. 2, one balance weight 1 is located at the center of the first crank throw 3 and left of the center of the second crank throw 4, the other balance weight 1 is located at the center of the third crank throw 5 and right of the center of the fourth crank throw 6, the centers of the first crank throw 3 and the second crank throw 4 are located at the left of the disturbance moment acting point 2, and the centers of the third crank throw 5 and the fourth crank throw 6 are located at the right of the disturbance moment acting point 2 (the dotted line is the central line of the balanced crankshaft).

As shown in fig. 3, the axis of one of the balance weights 1 forms an angle of 45 ° with the axis of the fourth crank throw 6 of the balanced crankshaft, and the axis of the other balance weight 1 forms an angle of-45 ° with the axis of the fourth crank throw 6 (the dotted line in the figure is the centerline of the balanced crankshaft).

The operation principle of the balanced crankshaft applied to a four-row symmetrical balanced compressor is further explained as follows:

two balance blocks with opposite directions and equal mass are respectively arranged at two shaft ends of the crankshaft. Because the inertia force of the four-row symmetrical balance compressor can be solved by the equal reciprocating mass of the two sides during the operation process, but the reciprocating moment is only solved by the crankshaft balance weight because the distance between the cylinder row and the action point exists. The four-row symmetrical reciprocating inertia moment coupling can be counteracted in the-45-degree direction through analysis. After the reciprocating mass of the unit obtains the horizontal disturbance moment, the horizontal disturbance moment of the unit is balanced by using the rotation inertia moment of the balance block. And calculating to obtain the position of the mass center of the balance weight, and superposing the moments generated by the two balance weights. So that the unit can realize the balance of the moment when the crankshaft rotates to any angle. As shown in fig. 4, fig. 4 is a schematic diagram of a relationship between a torque and a counterweight torque, wherein a curve with a starting point above is a schematic diagram of an effect of superposition of the counterweight torques, and a curve with a starting point below is a schematic diagram of an effect of summation of the torque.

In a reciprocating compressor, the reciprocating compressor includes a cylinder and a balanced crankshaft disposed in the cylinder, where the balanced crankshaft is the balanced crankshaft in the above embodiment.

In this specification, the invention has been described with reference to specific embodiments thereof. It will, however, be evident that various modifications and changes may be made thereto without departing from the broader spirit and scope of the invention. The specification and drawings are, accordingly, to be regarded in an illustrative rather than a restrictive sense.

Claims

1. A balanced crankshaft is characterized in that two sides of a disturbance torque action point of the balanced crankshaft are respectively provided with a balanced block;

the two balance blocks have equal mass, opposite radial directions of the axes and opposite directions of mass centers;

the axis of one balance weight and the axis of one crank throw in the balance type crankshaft form an included angle of 45 degrees, and the axis of the other balance weight and the axis of the crank throw form an included angle of-45 degrees.

2. A reciprocating compressor comprising a cylinder block and a balanced crankshaft disposed within said cylinder block, wherein said balanced crankshaft is the balanced crankshaft of any one of claim 1.