CN201301810Y - Compressor - Google Patents

Abstract

The utility model discloses a compressor, which comprises a pump body component arranged in a casing. The compressor is characterized in that the pump body component comprises a cylinder, a piston, a crankshaft, an upper bearing and a lower bearing, wherein the piston eccentrically rotates in the cylinder, the crankshaft is used with the piston and drives the piston to rotate, the upper bearing and the lower bearing support the crankshaft and form a closed space with the cylinder, the piston is provided with an inner flange, and the eccentric portion of the crankshaft is provided with a boss which extends to the lower side of the inner flange. On the basis of operation principle of the prior rotating compressor and driving properties of moving components of the pump body, the compressor reduces energy consumption of the moving components, increases lubricating performance among the motion components and reduces friction loss, and finally achieves the purposes of reducing energy consumption of the compressor, increasing coefficient of performance of components of the pump body and reduces vibration.

Description

Compressor

Technical field

The utility model relates to a kind of compressor, more particularly, relates to a kind of compressor that is used for aircondition.

Background technique

As shown in Figure 7, existing compressor comprises the pump housing parts that are built in shell 1, the bent axle 2 of its running of driving that these pump housing parts comprise cylinder 4, make the piston 5 of eccentric rotation in cylinder 4, use with piston 5 couplings, supports bent axle 2 and forms the metal (upper 3,6 of enclosed volumes with cylinder 4.

Existing rolling rotor type compressor pump housing parts of Shi Yonging, rolling piston upper and lower port edge generally carry out chamfered and form chamfering 51 (seeing shown in Figure 1), thereby the formation of being convenient to oil film like this reduces the friction of piston and respective cylinder parts.In addition, add groove 23 (seeing shown in Figure 2) in two ends about in the of 21, can reduce the friction at bent axle and corresponding part serious wear place at the eccentric position of bent axle 2.Though above structure has played certain effect to reducing friction, but design along with the miniaturization compressor, especially under the bigger situation of suction and discharge pressure, because rolling piston thickness is bigger, centrifugal force causes vibrating big phenomenon greatly, and power consumption is bigger, causes the also relatively large problem of compressor power consumption, is unfavorable for the high efficiency design of light duty compressor.

In addition, also have rolling piston is made relatively thinner structure, but can cause the generation of refrigerant from the exhaust port leakage phenomenon like this, therefore, upper bearing (metal) 3 exhaust ports 31 are made into the structure (as Fig. 3) of D shape exhaust port.Because piston is thinner, thereby alleviated the quality of rolling piston, reduced action of centrifugal force, finally played good effect reducing vibration and reducing power consumption.But because the upper bearing (metal) exhaust port adopts extrusion process, take above-mentioned D shape vent structure, its structural manufacturing process complexity, cost is higher; To leak in order preventing in addition, if the exhaust port aperture is reduced, can to cause exhaust resistance bigger, be unfavorable for the raising of pump housing performance, if exhaust port is moved to position near cylinder wall, the phenomenon that can cause cylinder clearance volume to increase again occurs.

Along with the carrying out of compressor with rolling rotor miniaturization machine exploitation, under the situation that the cylinder structure size remains unchanged, reduce the crankshaft eccentric distance, increase rolling piston thickness, thereby the problem that compressor power input raises and causes the coefficient of performance to descend can occur.Especially in high frequency running, under the bigger situation of suction and discharge pressure, vibration of compressor and power are all bigger, produce the lower phenomenon of the coefficient of performance thereupon.

Summary of the invention

The utility model is intended to address the above problem, its purpose is to provide a kind of like this compressor, the transmission performance that it has improved present rotary compressor pump housing parts reduces vibration of compressor and reduces bent axle and the abrasion of rolling piston, improves the coefficient of performance of compressor pump body component.

The purpose of this utility model is achieved in that a kind of compressor, comprise the pump housing parts that are built in shell, the bent axle of its running of driving that these pump housing parts comprise cylinder, make the piston of eccentric rotation in cylinder, use with the piston coupling, support bent axle and form the metal (upper of enclosed volume with cylinder, it is characterized in that: described piston is provided with inward flange, and the eccentric position of bent axle is provided with the boss that extends to above-mentioned inward flange below.

Described inward flange is located at the piston upper end-hole, and the piston upper-end surface extends to the width that can cover exhaust port at least in the compressor operation process fully by the inward flange upper surface.

Described piston cooperates installation with the crankshaft eccentric position, leaves the gap of 0.5mm-15mm between the inward flange lower edge of piston and the crankshaft eccentric portion boss upper surface.

The thickness of described inward flange is the 2%-30% of depth pistion, and the height of projection of inward flange is the 20%-80% of piston thickness.

Described inward flange hoop is located at piston upper end-hole inboard, and the cross section is square, trapezoidal or triangle.

Boss upper-end surface, described eccentric position is downward-sloping.

The oblique angle that dips down of boss upper-end surface, described eccentric position is more than or equal to 0 ° and less than 90 °.

The edge of described piston upper and lower port is a chamfering structure.

The utility model is based on the transmission of existing rotary compressor running principle and pump housing moving element, reduced energy consumption to moving element, increased lubricity between moving element to reduce frictional loss, finally reach and reduce the compressor power consumption, the purpose that improves pump housing component capabilities coefficient and reduce to vibrate.

Description of drawings

Fig. 1 is existing rolling piston sectional drawing;

Fig. 2 is the structural representation of existing bent axle;

Fig. 3 is the existing plan view of going up axle;

Fig. 4 is a piston sectional drawing of the present utility model;

Fig. 5 is the structural representation of bent axle of the present utility model;

Fig. 6 is that the utility model piston and bent axle cooperate the mounting structure schematic representation;

Fig. 7 is the whole sectional drawing of compressor.

Embodiment

The utility model is a kind of compressor, below in conjunction with drawings and Examples the utility model is further specified, but the utility model is not limited to this specific examples.

The basic structure of compressor of the present utility model also as shown in Figure 7, comprise the pump housing parts that are built in shell 1, the bent axle 2 of its running of driving that these pump housing parts comprise cylinder 4, make the piston 5 of eccentric rotation in cylinder 4, use with piston 5 couplings, support bent axle 2 and form the metal (upper 3,6 of enclosed volumes with cylinder 4.

The utility model is at small-sized machine, on the basis of existing common rolling rotor type compressor piston and crankshaft structure design, as shown in Figure 4, piston 5 at pump housing parts is provided with inward flange 52, the purpose of this structure is that the quality of piston 5 alleviates greatly, thereby reduce the centrifugal force in the running, reduce vibration of compressor.This inward flange 52 is located at piston 5 upper end-hole, and the piston upper-end surface prolongs certain width by the inward flange upper surface, makes the piston upper-end surface can cover exhaust port fully at least in the compressor operation process.Like this, the upper-end surface width of piston 5 can be approaching with the piston of prior art, and the quality of piston 5 can alleviate, and can prevent that refrigerant is by letting out in upper bearing (metal) 3 exhaust ports 31.

Preferably, as shown in Figure 4, the thickness a of inward flange 52 is the 2%-30% of piston 5 height, and height of projection b is the 20%-80% of piston 5 thickness.Inward flange 52 hoops are located at piston 5 upper end-hole inboards, do not carry out chamfered as piston 5 upper end-hole, then the cross section of flange 52 can be square or be trapezoidal, and as the edge of piston upper and lower port all carrying out chamfered, then the cross section of inward flange 52 can be trapezoidal or triangle again.

As shown in Figure 5, be provided with the boss 22 that extends to below the above-mentioned inward flange 52 at the eccentric position 21 of bent axle 2.Boss 22 upper-end surfaces are tilted to down, its tilt angle is more than or equal to 0 ° and less than 90 °, make between boss 22 and the inward flange 52 and have certain interval, can reduce the friction of bent axle 2 and piston 5 like this, and make lubricant oil keep good flowing property, the final compressor power consumption that reduces improves its pump housing coefficient of performance.

Fig. 6 is that piston 5 cooperates the position view after installing with the eccentric position 21 of bent axle 2.As shown in Figure 6, leave the gap of 0.5mm-15mm between inward flange 52 lower edges of piston 5 and crankshaft eccentric portion boss 22 upper surfaces, same, crankshaft eccentric shaft boss 22 lower surfaces and piston 5 lower end surfaces also keep certain interval.

The chamfering structure at piston 5 upper and lower port edges in conjunction with the groove 23 of being located at crankshaft eccentric portion two ends about in the of 21, can be strengthened the oil return performance, thereby reduces piston 5 and the friction of bent axle 2 and the friction of piston 5 and metal (upper face.

When piston 5 cooperates when running such as Fig. 6 with bent axle 2, lubricant oil flows into gap between bent axle 2 and the piston 5 by bent axle 2 oil outlets along the plane of inclination of boss 22.Because piston 5 is provided with inward flange 52, under the situation that does not change the exhaust pore size, can effectively prevent the coolant leakage in the exhaust port and the decreased performance that causes, piston 5 centrifugal force are effectively reduced in rotation process simultaneously.In addition, piston 5 internal surfaces and bent axle 2 area of contact are less, and frictional loss is reduced, and have finally played the purpose that reduces the compressor power consumption and reduce vibration of compressor.

Claims (8)

1. compressor, comprise the pump housing parts that are built in shell, the bent axle of its running of driving that these pump housing parts comprise cylinder, make the piston of eccentric rotation in cylinder, use with the piston coupling, support bent axle and form the metal (upper of enclosed volume with cylinder, it is characterized in that: described piston is provided with inward flange, and the eccentric position of bent axle is provided with the boss that extends to above-mentioned inward flange below.

2. compressor according to claim 1 is characterized in that: described inward flange is located at the piston upper end-hole, and the piston upper-end surface extends to the width that can cover exhaust port at least in the compressor operation process fully by the inward flange upper surface.

3. compressor according to claim 1 is characterized in that: described piston cooperates installation with the crankshaft eccentric position, leaves the gap of 0.5mm-15mm between the inward flange lower edge of piston and the crankshaft eccentric portion boss upper surface.

4. compressor according to claim 1 is characterized in that: the thickness of described inward flange is the 2%-30% of depth pistion, and the height of projection of inward flange is the 20%-80% of piston thickness.

5. compressor according to claim 1 is characterized in that: described inward flange hoop is located at piston upper end-hole inboard, and the cross section is square, trapezoidal or triangle.

6. compressor according to claim 1 is characterized in that: boss upper-end surface, described eccentric position is downward-sloping.

7. compressor according to claim 1 is characterized in that: the oblique angle that dips down of boss upper-end surface, described eccentric position is more than or equal to 0 ° and less than 90 °.

8. compressor according to claim 1 is characterized in that: the edge of described piston upper and lower port is a chamfering structure.

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