KR0173575B1 - Scroll type fluid machinery - Google Patents

Abstract

The present invention relates to a scroll type fluid machine, and is a so - called co - rotatory scroll type fluid machine, which is a compression type by synchronous rotary motion of an orbiting scroll member and a fixed scroll member, A plurality of position setting pins and a fastening member are inserted and fixed to penetrate the edges of the high / low pressure separating plate, the distance adjusting member, and the upper frame, An upper bearing is press-fitted into a central portion of a high / low pressure separating plate formed with a discharge port for rotating the fixed scroll member, and an oil collection groove for collecting lubricating oil discharged from the discharge port together with the compressed fluid, A plurality of supply passages formed in a spiral shape in the upper bearing, And the upper bearing is lubricated without a separate device to enable synchronous rotational movement between the orbiting scroll member and the fixed scroll member. By using the distance adjusting member, the axial interval is maintained constant to maximize the efficiency, It is effective to make the operation possible.

Description

Corotting scroll fluid machine

BACKGROUND OF THE INVENTION 1. Field of the Invention [0001] The present invention relates to a scroll compressor, and more particularly, to a corotating scroll type fluid machine for maximizing airtightness between a fixed scroll member and an orbiting scroll member of a scroll compressor.

Generally, the basic principle of scrolling developed and applied in various fields such as compressor, vacuum pump, inflator, engine, etc. was first presented by Leon Creux in France and patented in USA in 1905, Was developed for Helium Compressor by Little Co., Ltd. Especially, scroll compressor for automobile air conditioner was first developed by Sanden of Japan in 1981, and for scroll compressor for air conditioning, Hitachi of Japan, The commercialization of the scroll compressor in 1983 was the most important factor in the practical use of the scroll compressor because of the development of the high precision CNC machining technology for the scroll wrap machining and the improvement of the efficiency of the compressor improves the performance of the entire refrigeration system, From the viewpoint of economical efficiency, high efficiency of compressors, technical improvement of low noise and low vibration Could.

The overall shape of the scroll device is a structure in which the circular end plate and the spiral or involute wrap are integrated. The orbiting scroll member is rotated 180 degrees with respect to the relative fixed scroll member, and the two scroll members are fitted together, A plurality of line abutting portions are formed between the covers and the orbiting scroll member is operated by orbiting along a predetermined orbit by the eccentric shaft and the outward coupling which functions to prevent rotation. A line-of-contact is formed between the sides of the respective members and an axial bias of the orbiting scroll member forms a sealing surface contact between the two scroll members, wherein fluid-tight, closed, crescent- And between the two members that are ideally operating, there is no relative rotation, i.e., a curve translational motion. At this time, a plurality of crescent-shaped fluid pockets are formed in an arbitrary area of the scroll compressor including the suction fluid, up to a region where any discharge port including the discharge pressure is formed. As the sealing pocket moves toward the discharge port, the volume of the sealing pocket changes, so that even when there are multiple pairs of sealing pockets, as in the case of at least one pair of sealing pockets at any one time, And the pressure in the discharge port region in the scroll device becomes higher than the pressure in the region containing the suction fluid.

At this time, the two types of contact portions include tangential contact portions extending in the axial direction between the side of the scroll member and the moving line contact portion caused by the radial force between the side surfaces or spiral surfaces of the two scroll members, Is expressed as a sealing surface contact caused by net axial stresses between the sealing surfaces which form a movable, sealed, crescent-shaped fluid pocket between the scroll members. Therefore, effective sealing of the two types of contact surfaces is a necessary and sufficient condition for achieving high compression efficiency.

The leakage of the compressed gas and the wear of the material in the scroll type compressor are caused by a large or no gap generated between the fixed scroll member and the orbiting scroll member. The shape of the gap is largely divided between the side surfaces of the two scroll members And an axial gap generated between the bottom surface of the fixed scroll member and the upper surface of the orbiting scroll member. In order to reduce the current radial clearance, a method of using a compliance coupling between the rotary shaft and the orbiting scroll has been developed and a structure has been developed in which the axial clearance has a backpressure chamber above or below each scroll member. The back pressure chamber structure allows the back pressure chamber pressure to push the scroll member in a direction opposite to this direction when the compressed gas in the compression chamber pushes the scroll member in the axial direction, thereby controlling the axial gap.

Further, a more specific conventional example will be described in detail with reference to the accompanying drawings.

1 shows a scroll fluid machine in which a sealing shell A is welded to an upper chamber 100, an intermediate chamber 90 and a lower chamber 110, A high / low pressure separating plate 60 is welded to the sealing shell A so as to prevent the fixed scroll member 30 from moving in the upward direction due to internal pressure, The orbiting scroll member 30 is mounted on the lower portion of the low pressure separating plate 60 and the orbiting scroll member 40 is sealed to form the spiral compression chamber 20 for compressing the fluid in the fixed scroll member 30. [ The lower portion of the fixed scroll member 30 is seated on the upper end of the upper frame 50 and the tongue spring 140 is inserted into the groove formed in the upper end of the upper frame 50, Thereby reducing the load generated between the member 30 .

The upper frame 50 and the lower frame 120 supporting the rotary shaft 70 are firmly fastened by the fastening members 153 inserted between the flanges 150 welded to the intermediate chamber 90.

An upper bearing 53 is press-fitted into the upper frame 50. The center of the lower frame 120 is formed as a lower bearing 122 and the upper bearing 53 and the lower bearing 122, And the upper portion of the rotary shaft 70 is connected to the inside of the orbiting scroll member 40. The upper portion of the rotary shaft 70 is inserted into the outer peripheral surface of the rotary shaft 70, And a radial coupling 71 which serves to stably absorb the inertial force and the tilting moment in the direction of the axis perpendicular to the axis of rotation 70 generated between the upper frame 50 and the lower frame 120, The rotor 154 is integrally formed at a central portion thereof by press fitting. The gap between the rotor 154 and the stator 152 is maintained at a predetermined interval.

In the recessed grooves 41a and 41b formed between the upper end of the upper frame 50 and the orbiting scroll member 40, there is formed an overt coupling coupler for converting the rotational motion of the rotary shaft 70 into a curved translation movement 80 are mounted.

A back pressure chamber 65 is formed at an inner upper end of the high / low pressure separation plate 60. A discharge port 14 is formed in the upper portion of the fixed scroll member 30 to disperse and discharge the compressed fluid. And a discharge pipe 112 for discharging the fluid discharged from the discharge port 14 to the outside of the compressor through a high pressure tank 111 in a predetermined space is provided at one side of the upper chamber 100, A check valve 10 for preventing the backflow of the fluid from the tank 111 is attached to the upper side of the discharge port 14 and the lower contact surface of the high / low pressure separation plate 60 and the fixed scroll member 30 And a seal member 130 for preventing leakage is provided between the upper contact surfaces in the axial direction.

2, a plurality of protrusions 32 are formed at predetermined intervals along the circumferential direction of the fixed scroll member 30, and the protrusions 32 formed on the upper frame 50, The protruding portion 32 is inserted so that the fixed scroll member 30 is not rotated by the centrifugal force when the orbiting scroll member 40 is pivoted. When the fixed scroll member 30 is biased in the axial direction, the side surfaces of the projecting portion 32 formed on the outer peripheral surface and the side surface 51 of the recessed portion 52 of the upper frame 50 are slid together to form the fixed scroll member 30 Move up and down.

At this time, when the rotational force of the rotary shaft 70 is transmitted to the orbiting scroll member 40 in a state where the fixed scroll member 30 is fixed, the orbiting scroll member 80 is rotated by the orbiting- The fluid 40 is not pivoted but pivoted, thereby compressing the fluid.

Compressed and re-expanded as compared with the reciprocating compressor, the scroll compressor thus constructed minimizes leakage because it is effectively sealed by the respective contact surfaces, and is 10% more efficient than the reciprocating type, and the torque variation is about 1 / 10, and the simultaneous compression in a plurality of opposing pockets reduces the pressure generated vibration due to the unidirectional fluid flow, and the production cost is low by 10 to 20% Lightweight and small size.

However, in spite of the excellent performance of the scroll type compressor, the revolving scroll member may be rotated by a centrifugal force acting on the orbiting scroll member at a predetermined eccentric rotation with respect to the rotation axis center line, In order to solve this problem, a balance weight is attached to the rotor to solve unbalance caused by the centrifugal force. In other words, in order to solve the unbalance due to the centrifugal force, However, in actual operation, the effect of vibration and noise is limited due to the fact that the effect is not constant depending on the operating conditions. Particularly, since the balance weight is required in a large amount compared to the minimum balance weight required for the centrifugal force of the rotor itself, the size of the compressor is increased due to unnecessary waste of material and waste of space, .

SUMMARY OF THE INVENTION Accordingly, the present invention has been made keeping in mind the above problems occurring in the prior art, and it is an object of the present invention to provide a scroll fluid machine in which the center of gravity of a fixed scroll member, The orbiting scroll member rotates with respect to the center point of the orbiting scroll member so that the center of gravity of the member can always rotate with respect to each center point while maintaining a constant distance between the center points of the orbiting scroll member, The present invention provides a corotating scroll type fluid machine in which rotation is performed based on a reference, but the intervals between the centers are constant.

According to an aspect of the present invention, there is provided a method for transmitting power to a fixed scroll member using a rotating movement of an orbiting scroll member, the method comprising: forming a space between a pair of scroll members, And wherein each of the recessed grooves is equipped with an opposed crowned coupling and the protrusion formed on the shouldered coupling is used for power transmission to determine the direction of the scroll member, In order to enable self-lubrication without requiring a separate pump during the rotation of each scroll member, the refrigerant and lubricating oil are simultaneously compressed in the compression chamber, and the compressed mixed fluid flows into the high-pressure tank through the discharge port, The refrigerant is discharged to the outside through the discharge pipe, and the separated lubricating oil is dropped by its own weight so as to remain in the oil collecting groove. And a spiral flow passage connected to the oil collection groove is formed in the upper bearing so that the protrusion of the fixed scroll member is rotated to supply and recover the lubricating oil through the flow passage to eliminate the noise and vibration generated in the compressor .

1 is a vertical sectional view of a conventional scroll fluid machine

2 is a sectional view taken along the line A-A in Fig. 1 showing the axial bias guide portion of the fixed scroll member

Figure 3 is a vertical section of a scroll fluid machine according to the invention

4 is a sectional view taken along the line A-A in Fig. 3

Fig. 5 is an enlarged detail view of part B of Fig. 3

FIG. 6 is an enlarged detail view of the portion D in FIG.

Fig. 7 is an explanatory diagram showing a state in which a pair of scroll members performs synchronous operation; Fig.

FIG. 8A is a partial longitudinal sectional view showing the internal pressure state in the compression chamber immediately after the start of operation, and FIG. 8B is a partial vertical sectional view showing the back pressure operating state in the back pressure chamber during operation. FIG.

DESCRIPTION OF REFERENCE NUMERALS

a, x: clearance 10: distance adjustment member

] 11: Upper bearing 12: Feeding passage

13: return flow passage 14: discharge port

62: Oil collecting groove 141: Lubricant particle

142: fluid 151: fastening member

155: fastening member 156: gasket

160: Position setting pin 160a: Disengaging groove

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the accompanying drawings.

3 is a view showing an embodiment according to the present invention. Unlike the conventional high / low pressure separation plate 60 welded and fixed to the sealing shell A, the high / The distance adjusting member 10 is mounted around the outer periphery of the pair of the scroll members 30 and 40 so as to support the space between the upper frame 50 and the high / A plurality of position setting pins 160 are inserted and supported to support the distance adjusting member 10 through the edges of the high / low pressure separating plate 60, the distance adjusting member 10 and the upper frame 50, The center and the upper bearing 11 of the main bearing 51 are fixed to the high and low pressure separating plate 60 and the upper frame 50 in order to maintain a predetermined distance and an accurate eccentricity x, The two positioning holes 160 are formed in a predetermined position with respect to the center point of the position setting pin 160 When the mouth is. This is simply a hole machined to the eccentricity x, and is held by inserting the position setting pin 160 therein.

At this time, a separation groove 160a having an internal thread is formed at an upper center portion of the position setting pin 160 so that the position setting pin 160 can be easily separated using a tool when the positioning pin 160 is separated.

4, a fastening member 155 for vertically applying a vertical force to the upper and lower edge positions as well as the left and right positions at which the position setting pins 160 are inserted is rigidly fixed, The gasket 156 is inserted into the fastening member 155 so as to press the separator 60 and effectively prevent the leakage of the pressurized fluid from the high-pressure tank 111.

5, a coupling 80 is inserted and mounted between the lower end of the fixed scroll member 30 and the upper end of the orbiting scroll member 40, The bearing 11 is press-fitted into the central portion of the high / low pressure separating plate 60 in which the discharge port 14 is formed to support the fixed scroll member 30. The compressed fluid 142 is discharged from the discharge port 14 An oil collecting groove 62 for collecting the lubricating oil 141 to be discharged into the upper bearing 11 is formed around the discharge port 14 in the center upper portion of the high / low pressure separating plate 60.

6, a plurality of spiral flow paths 12 and 13 connected to the oil collecting groove 62 are formed in the upper bearing 11 so as to have a predetermined curve in the upward and downward directions The supply path 12 and the recovery path 13 correspond to this.

A main bearing 51 is inserted into the upper frame 50 to support the rotary shaft 70 and a fastening member 151 is inserted between the rotary shaft 70 and the lower end of the orbiting scroll member 40 So that the rotational force of the rotary shaft 70 is transmitted to the orbiting scroll member 40. A small gap a in the axial direction is generated between the pair of scroll members 30, The center line of the orbiting scroll member 40 and the center line of the fixed scroll member 30 are eccentrically spaced at a predetermined interval. The eccentricity amount x is determined according to the basis diameter of the wrap curve and the wrap thickness, The rotational center of the member 30 corresponds to the value of this eccentric amount x.

When the scroll fluid machine thus constructed operates, the compression between the two scroll members 30 and 40 proceeds as follows, as shown in FIG. 7, and the rotation of the rotary scroll 70 causes the orbiting scroll When the member 40 is pivoted, the fixed scroll member 30 is rotated about the eccentricity amount x along the upper bearing 11 through the welded coupling 80. At this time, The orbiting scroll member 40 and the fixed scroll member 30 compress the fluid while performing the synchronous operation at the same number of revolutions so as to enhance the compression efficiency. The center line of the orbiting scroll member 40 and the fixed scroll member 30 Since the center line of the fixed scroll member 30 is eccentric by an eccentric amount x of a predetermined interval by the position setting pin 160, the center of rotation of the fixed scroll member 30 corresponds to the value of the eccentricity amount x.

At this time, the most important role of the above-mentioned coupling 80 is to allow the pair of scroll members 30 and 40 to always move radially while maintaining a predetermined direction, When the lap lower end portion 31 and the lap upper end portion 42 and the fixed scroll sealing surface 35 and the orbiting scroll sealing surface 45 are closely contacted with each other without any gap between the lower end portion 31 and the orbiting scroll member 40, The lap upper end portion 42 and the fixed scroll sealing surface 30 are formed at the initial stage at the time of initial start-up because the undesired compression causes an excessive starting load between the two scroll members 30, It is necessary to keep the eccentric amount x between the revolving scroll sealing surface 45 and the revolving scroll sealing surface 45. When the amount of eccentricity x is large, leakage occurs on the wall surface. When the amount of eccentricity x is small, , 40). At this time, the position setting pin 160 is inserted into a predetermined groove formed between the high / low pressure separating plate 60 and the upper frame 50, so that the eccentricity amount x is kept constant.

8A, the internal pressure generated in the compression chamber 20 at the time of initial startup pushes the fixed scroll member 30 toward the high / low pressure separation plate 60. At this time, Becomes zero. 8B, the compressed fluid is supplied from the compression chamber 20 to the back pressure chamber 65 through the flow passage 34, and a small amount of the compressed fluid is supplied to the back pressure chamber 65. As a result, When the scroll member 30 is pressed downward, the value of the clearance a becomes maximum instantaneously, and the leakage of the fluid is completely blocked by the seal member 1030. When the seal member 1030 is in an equilibrium state between the internal pressure and the back pressure Low pressure separating plate 60 and the upper frame 50. The upper and lower frames 50 and 50 are fixed to the upper and lower frames 50 and 50 by means of a fastening member 155 .

6, the lubricating oil 141 is mixed with the fluid 142 at the time of compressing the fluid 142 in the compression chamber 20, compressed and mixed with the lubricating oil 141 through the discharge port 14 A pressure drop is generated as it is diffused in the high pressure tank 111. At this time, the compressed fluid 142 and the lubricant particles 141 are separated by the difference in size so that the compressed fluid 142 having a small particle size is discharged to the outside through the discharge pipe 112, The lubricating oil 141 in the oil collecting groove 62 flows into the oil collecting groove 62 through the spiral supply passage 12 formed in the upper bearing 11 And is moved to the recovery flow path (13) by rotation of the fixed scroll member (30) to lubricate the entire inner surface of the upper bearing (11).

At this time, the outer circumferential surface of the discharge port (14) formed at the upper center of the fixed scroll member (30) slides along the inner peripheral surface of the upper bearing (11) in the circumferential direction and the axial direction component, Contact linear velocity is related to the back pressure action of the back pressure chamber 65 and is faster than the linear velocity in the axial direction.

The lubricating oil 141 that has passed through the recovery passage 13 while sliding is moving between the upper bearing 11 and the outer peripheral surface of the discharge port 14 moves between the upper bearing 11 and the discharge port 14 The lubricating oil 141 is distributed on the outer circumferential surface of the discharge port 14 and the lubricating oil 141 is lubricated on the outer circumferential surface of the discharge port 14 and the inner circumferential surface of the upper bearing 11 by the rotation of the fixed scroll member 30. [ The lubricating oil 141 is spread in the spiral groove portion formed on the inner peripheral surface of the upper bearing 11 while the lubricating oil 141 is diffused and thus a larger surface tension is applied to the lubricating oil 141 which is lodged in the spiral groove portion. That is, there is a close relationship between the linear velocity in the circumferential direction and the helical groove and the surface tension, and these three variables act simultaneously to spiral the lubricant 141. As the circulation continues during the operation of the compressor, the lubricating oil 141 of the upper bearing 11 can be smoothly supplied. In particular, the lubricating oil 141 can be easily fixed to the upper bearing 11 The lubricating oil 141 can be injected between the outer diameter of the discharge port 14 of the scroll member 3.

As described above, according to the present invention, it is possible to maximize the efficiency by preventing leakage in a smooth operation state, thereby eliminating the swinging motion of the orbiting scroll member, thereby reducing vibration and supplying the lubricating oil without any additional device between the fixed scroll member and the upper bearing Thereby smoothly operating the compressor in synchronous rotation between the orbiting scroll member and the fixed scroll member, and at the same time, simplifying the structure, thereby reducing the cost and, in particular, reducing the noise caused by the vibration, thereby enabling silent operation with low noise and low vibration It is effective.

Claims (4)

A sealing shell A composed of an upper chamber 100 and an intermediate chamber 90 and a lower chamber 110 and a fixed scroll member 30 and an orbiting scroll member 40 in the sealing shell A, Pressure fluid separating plate 60 is fixed to the fixed scroll member 30 in the state where the upper frame 50 and the high / The distance adjustment member 10 is mounted around the periphery of the pair of scroll members 30 and 40 to support the space between the high and low pressure separation plates 60 and 60 and the distance adjustment member 10 A plurality of position setting pins 160 are inserted through the edges of the upper frame 50 so as to be symmetrical to each other to maintain a constant eccentricity x and a plurality of Low pressure separating plate 60 by inserting and fastening the fastening member 155 and a vertical force is applied to the high / Low pressure separating plate (not shown) having a discharge port 14 formed therein for rotation of the fixed scroll member 30, and a low-pressure separating plate The upper bearing 11 is press-fitted into the central portion of the upper bearing 11 to support the fixed scroll member 30 and the lubricating oil 141 discharged together with the compressed fluid from the discharge port 14 is supplied to the upper bearing 11 And a coupling member 151 is inserted between the rotary shaft 70 and the lower end of the orbiting scroll member 40 so that the rotary shaft 70 Is adapted to transmit a rotational force of the orbiting scroll member (40) to the orbiting scroll member (40) so as to allow synchronous rotational movement between the fixed scroll member (30) and the orbiting scroll member machine. 2. The apparatus according to claim 1, wherein a separation groove (160a) having an internal thread is formed at an upper center portion of the position setting pin (160) so as to be separated by a tool when the position setting pin (160) Wherein the scroll fluid machine is a scroll compressor. The upper bearing (11) according to claim 1, wherein the lubricating oil (141) collected in the oil collecting groove (62) is supplied to the upper bearing (11) Wherein a plurality of spiral supply passages (12) and return passages (13) connected to the oil collecting grooves (62) are formed in the interior of the oil collection groove (62). The scroll fluid machine of claim 1, wherein the fastening member (155) is fitted with a gasket (156) so as to prevent leakage of the compressed fluid (142) from the high pressure tank (111).