CN101852208A

CN101852208A - Radial seal structure for scroll compressor

Info

Publication number: CN101852208A
Application number: CN 201010193023
Authority: CN
Inventors: 刘兴旺; 姚淑婷; 齐学义; 李超; 赵嫚; 刘振全; 余建平; 陈叔平; 荆兵; 王小娟; 史洁; 王彩鹃
Original assignee: Lanzhou University of Technology
Current assignee: Lanzhou University of Technology
Priority date: 2010-05-27
Filing date: 2010-05-27
Publication date: 2010-10-06

Abstract

The invention relates to a radial seal structure for a scroll compressor. The invention aims to reduce the radial leakage between adjacent compression chambers of the scroll compressor and enhance the polytropic efficiency of the scroll compressor. The structure of the invention is as follows: on the top land of flexible scroll teeth and static scroll teeth, a rectangular tank is arranged from the position, which is a distance (e) away from the inner wall surface (in) of the scroll teeth in the wall thickness direction (D) of the scroll teeth, to the position, which is a distance (e) away from the outer wall surface (out) of the scroll teeth in the reverse direction of the wall thickness direction (D) of the scroll teeth; the ratio of distance (e) to wall thickness (t) of the scroll teeth is greater than or equal to 0.05 and smaller than or equal to 0.07; and the wall thickness (t) of the scroll teeth is greater than or equal to 3.5 mm and smaller than or equal to 8.5 mm.

Description

The radial seal structure of scroll compressor

Technical field

The present invention relates to the sealing of scroll compressor dynamic vortex tooth.

Background technique

At present, mainly contain three kinds in order to the mechanism that realizes the radial seal between scroll compressor vortex tooth tooth top and the scroll bottom land:

(1) not tape spool to the orbiting and fixed scroll engaging mechanism of controlling mechanism, the tooth top surface of its dynamic vortex tooth and static vortex tooth all is a smooth surface, on the orbiting and fixed scroll without any controlling mechanism, during compressor operating, suffered axial gas power can make the axial clearance Ca between dynamic vortex tooth tooth top and fixed scroll bottom land on the moving scroll, axial clearance Cb between the axial clearance Ca between static vortex tooth tooth top and moving scroll bottom land and moving scroll plate upper surface and fixed scroll lower surface increases, cause radial leakage by axial clearance Ca and the leakage by axial clearance Cb to increase, the polytropic efficiency of compressor reduces.

(2) the orbiting and fixed scroll engaging mechanism of band back pressure cavity, offer the back-pressure balance hole at moving scroll bottom land, gas in the compression chamber can be scurried in the back pressure cavity at the moving scroll back side by the back-pressure balance hole, gas in the back pressure cavity applies a direction and the suffered opposite counterpressure of axial gas force direction of moving scroll to moving scroll, can make the axial clearance Cb between scroll plate upper surface and fixed scroll lower surface is zero, but can not guarantee simultaneously that axial clearance Ca and the axial clearance Ca between static vortex tooth tooth top and moving scroll bottom land between dynamic vortex tooth tooth top and fixed scroll bottom land are zero, still bigger by the radial leakage of axial clearance Ca.In addition, if end thrust is too big, will cause the friction power loss of moving scroll plate upper surface and fixed scroll lower surface contact position to increase; If end thrust is too small, the axial clearance Cb between then moving scroll plate upper surface and fixed scroll lower surface is greater than zero, and the leakage at this place can not get effective sealing.

(3) the orbiting and fixed scroll engaging mechanism of the tooth top band Stamping Steel Ribbon of sound scroll wrap, it is the Stamping Steel Ribbon made from self lubricating material in the tooth top embedding of dynamic vortex tooth and static vortex tooth, the gas force that acts on the Stamping Steel Ribbon bottom floats also Stamping Steel Ribbon and the applying of scroll bottom land vertically, gas leakage is played the throttling blocking action, thereby realize radial seal.But in wearing and tearing produce the trifling seal strip groove that enters mosaic seal, can make Stamping Steel Ribbon lose unsteady ability, sealing effect seriously descends.In addition, the working life of Stamping Steel Ribbon is short, causes the compressor maintenance frequent, uses inconvenience.

Summary of the invention

The objective of the invention is to reduce the radial leakage between the adjacent compression chamber of scroll compressor, improve the polytropic efficiency of scroll compressor.

The present invention is the radial seal structure of scroll compressor, respectively on the tooth top surface of dynamic vortex tooth and static vortex tooth, begin on apart from the tooth top surface between the position of e, to offer rectangle groove from scroll wrap outer wall out for position apart from scroll wrap internal face in along scroll wrap wall thickness direction D to edge and scroll wrap wall thickness direction D opposite direction apart from e, span apart from the ratio of e and scroll wrap wall thickness t is: 0.05≤e/t≤0.07, the span of scroll wrap wall thickness t is: 3.5mm≤t≤8.5mm.

Usefulness of the present invention is, axial clearance and the sound scroll wrap tooth top surface of not offering the radial seal structure of rectangle groove in sound scroll wrap tooth top surface offered under the condition that the axial clearance of the radial seal structure of rectangle groove equates, the radial leakage amount that sound scroll wrap tooth top surface is offered the sealing configuration of rectangle groove only account for sound scroll wrap tooth top surface do not offer rectangle groove sealing configuration the radial leakage amount 46%, reduce the radial leakage of scroll compressor greatly, improved the polytropic efficiency of scroll compressor.In addition, sound scroll wrap tooth top surface being offered the requirement of axial clearance Ca of the sealing configuration of rectangle groove can suitably loosen, thereby the processing and the assembly precision of the orbiting and fixed scroll have been reduced to a certain extent, can eliminate the friction between scroll wrap tooth top and scroll bottom land, more be applicable to non-lubricated vortex compressor.

Description of drawings

Fig. 1 is the plan view of the orbiting and fixed scroll of the present invention engagement, Fig. 2 be among Fig. 1 A-A to sectional drawing, Fig. 3 be among Fig. 2 B-B to sectional drawing, Fig. 4 be among Fig. 3 E to view, Fig. 5 be among Fig. 4 along C-C to sectional view.

Embodiment

Fig. 1 is a sound scroll wrap engagement plan view of the present invention, the I position is the contact position of moving scroll plate upper surface and fixed scroll lower surface among Fig. 1, it is zero that the moving suffered counterpressure of scroll can make the axial clearance Cb between scroll plate upper surface and fixed scroll lower surface, but guaranteeing that axial clearance Cb is under zero the condition, can not guarantee simultaneously that axial clearance Ca and the axial clearance Ca between static vortex tooth tooth top and the moving scroll bottom land between dynamic vortex tooth tooth top and the fixed scroll bottom land is zero.Fig. 2 has represented that the engagement of sound scroll wrap forms the situation of compression chamber, and bent axle drives moving scroll and does the revolution translation around fixed scroll center O O ' during work, has formed severally to cavity between the sound scroll wrap, and gas is compressed.Gas in hyperbaric chamber clearance C a vertically leaks to the low-pressure cavity adjacent with hyperbaric chamber.

As shown in Figure 3, Figure 4, the radial seal structure of scroll compressor of the present invention, respectively on the tooth top surface of dynamic vortex tooth and static vortex tooth, begin on apart from the tooth top surface between the position of e, to offer rectangle groove from scroll wrap outer wall out for position apart from scroll wrap internal face in along scroll wrap wall thickness direction D to edge and scroll wrap wall thickness direction D opposite direction apart from e, span apart from the ratio of e and scroll wrap wall thickness t is: 0.05≤e/t≤0.07, the span of scroll wrap wall thickness t is: 3.5mm≤t≤8.5mm.

As shown in Figure 4, the length direction of all rectangle grooves is all consistent with the molded lines direction F of scroll wrap, the span of the width b of rectangle groove is: 0.4mm≤b≤0.5mm, the span of the ratio of the length L of rectangle groove and width b is: 8≤L/b≤10 along the span of the ratio of the distance s of the molded lines direction F adjacent rectangle groove of scroll wrap and rectangle groove length L are: 1.1≤s/L≤1.25.Along the adjacent rectangle groove of scroll wrap wall thickness direction D is staggered mutually, along the span of the spacing c of scroll wrap wall thickness direction D adjacent rectangle groove and the ratio of width of rectangular b is: 1.6≤c/b≤1.8.As Fig. 4, shown in Figure 5, the rectangle groove depth d with span along the ratio of the spacing c of scroll wrap wall thickness direction D adjacent rectangle groove is: 0.5≤d/c≤0.7.

As shown in Figure 5, gas in the hyperbaric chamber under the promotion of pressure reduction by the hyperbaric chamber side direction low-pressure cavity side flow of compressor, when air-flow process scroll wrap tooth top axial clearance, because runner narrows down, speed increases, pressure reduces, be that pressure can change kinetic energy into, simultaneous temperature reduces, when gas entered rectangle groove, owing to the sudden enlargement of flow area produces violent vortex, the result of eddy current friction made most kinetic energy of air-flow be converted into heat energy, by the GAS ABSORPTION in the rectangle groove, the temperature of gas raises to some extent.As seen, after gas arrived rectangle groove through axial clearance, pressure just reduced certain value, so repeats said process, and the gas pressure in the rectangle groove reduces step by step, means that the thrust of gas leakage reduces step by step, has just reached the purpose that resistance is leaked.In addition, along the adjacent rectangle groove of scroll wrap wall thickness direction mutually the staggered gas that can effectively prevent along directly leaking into low-pressure cavity the gap of scroll wrap wall thickness direction between rectangle groove and rectangle groove.

Claims

1. the radial seal structure of scroll compressor, it is characterized in that respectively on the tooth top surface of dynamic vortex tooth and static vortex tooth, begin on apart from the tooth top surface between the position of (e), to offer rectangle groove from scroll wrap outer wall (out) apart from the position of scroll wrap internal face (in) along scroll wrap wall thickness direction (D) for distance (e) to edge and scroll wrap wall thickness direction (D) opposite direction, the span of the ratio of distance (e) and scroll wrap wall thickness (t) is: 0.05≤e/t≤0.07, the span of scroll wrap wall thickness (t) is: 3.5mm≤t≤8.5mm.

2. the radial seal structure of scroll compressor according to claim 1, all the molded lines direction (F) with scroll wrap is consistent to it is characterized in that the length direction of all rectangle grooves, the span of the width of rectangle groove (b) is: 0.4mm≤b≤0.5mm, the span of the ratio of length of rectangle groove (L) and width (b) is: 8≤L/b≤10 along the span of the ratio of the spacing (s) of molded lines direction (F) the adjacent rectangle groove of scroll wrap and rectangle groove length (L) are: 1.1≤s/L≤1.25.

3. the radial seal structure of scroll compressor according to claim 1, it is characterized in that along the adjacent rectangle groove of scroll wrap wall thickness direction (D) it being mutually staggered, along the span of the spacing (c) of scroll wrap wall thickness direction (D) adjacent rectangle groove and the ratio of width of rectangular (b) be: 1.6≤c/b≤1.8.

4. the radial seal structure of scroll compressor according to claim 1 is characterized in that the rectangle groove degree of depth (d) and span along the ratio of the spacing (c) of scroll wrap wall thickness direction (D) adjacent rectangle groove are: 0.5≤d/c≤07.