JP2001221169A - Multiple connection type scroll compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To solve problems of a swirel scroll with double teeth a through hole for a shaft, that: an outer diameter is enlarged because an autorotation prevention mechanism is obliged to be installed on the outside of a spiral lap in a constitutional requirement; durability of bearing load is lowered because gas compression load and centrifugal force of two pairs of compression mechanisms act in the same direction; and performance and durability are lowered because the rotating lap is formed integrally on both faces of end plates of the low rigidity swirel scroll to increase deformation at a time of machining and operation. SOLUTION: This multiple connection type scroll compressor has compression chambers formed in such a manner that two fixed scrolls with double teeth are meshed with two swirel scrolls. Each fixed scroll with double teeth is constituted by connecting back faces of end plate of two fixed scrolls having spirals of opposite winding direction to each other. In the swirel scroll, spiral projection of which planner shapes of rotating laps have respective equal mirror images, and a bearing boss having a rotating bearing arranged on load center and the through hole for a shaft which are erected on the edge plate. The multiple connection type scroll compressor has two pairs of the compression mechanism portions constituted of the shaft with two rotating shafts opposite to and eccentric with each other and an autorotation prevention mechanism.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a multi-connection scroll compressor suitable for increasing the capacity used in a refrigerating and air-conditioning compressor or an air compressor using gas as a working fluid.

[0002]

2. Description of the Related Art A scroll compressor is usually composed of a set of compression mechanisms forming two compression chambers. However, when the capacity of such a compressor is increased, the formation of the compression chambers is a constraint. The strength of the spiral wrap, the durability of the bearing which receives the centrifugal force of the orbiting scroll and the gas compressive load, and the size of the machine for processing the spiral wrap are also mentioned.

[0003] As a means of overcoming these constraints,
There is a means for increasing the total compressor capacity by combining a plurality of compression mechanism units satisfying the constraint conditions from the same idea as reducing the size per unit by using a plurality of compressors.
One of the arrangements in which a plurality of sets of compression mechanism parts are provided adjacent to each other is that two spiral wraps are provided on both surfaces of the end plate of the orbiting scroll.
2. Description of the Related Art Conventionally, a double-toothed orbiting scroll that is formed individually to constitute two sets of compression mechanism units has been proposed. Among these, as a well-known example of a double toothed orbiting scroll having a shaft through hole for passing a power transmission shaft through the center of the orbiting scroll, Japanese Patent Publication No.
126159 and JP-A-9-324770. However, there is no known example of a double-toothed fixed scroll in which two spiral wraps are provided on both sides of the center end plate of the fixed scroll to constitute two sets of compression mechanisms.

[0004]

The problem to be solved by the present invention is that, in a double-toothed orbiting scroll having a shaft through hole, a rotation preventing mechanism for imparting a revolving motion on a circular orbit to the orbiting scroll is constituted. There is a problem that the outer diameter of the compressor is greatly increased because it has to be provided on the outer periphery of the end plate protruding outside of the spiral wrap.

The bearing load increases further due to the increase in bearing load due to the simultaneous application of the gas compression loads for the two sets of compression mechanisms in the same direction, and the increase in the centrifugal force due to the increase in the weight of the orbiting scroll accompanying both teeth. There are problems that the durability is reduced and that the balancer that balances this centrifugal force becomes large.

Further, since the wraps are fixed to both surfaces of the end plate of the orbiting scroll and integrated, the axial movement of the orbiting scroll can be controlled to adjust the gap between the two wrap tips to seal. If this is not possible, it becomes difficult to control when the thrust force acting on the orbiting scroll is unbalanced, and there has been a problem that vibrations increase and reliability and performance decrease.

If wraps are provided on both sides of the end plate of the orbiting scroll, which has considerably lower rigidity than the frame supporting the wrap of the fixed scroll, the machining accuracy is greatly reduced, and at the same time, a large deformation due to a load applied during operation and a temperature change is caused. There is a problem that performance and durability deteriorate.

The present invention provides an air compressor and a refrigeration / air-conditioning compressor capable of simultaneously achieving a reduction in size and weight and an improvement in efficiency while securing reliability by dispersing bearing loads when increasing the capacity of the compressor. The purpose is to provide.

[0009]

Here, a plurality of sets of compression mechanisms are formed adjacent to one set of compression mechanisms forming two compression chambers, and at the same time, a power transmission shaft passes through the inside of the compression mechanisms. Means for solving the above-mentioned conventional problem with the double toothed orbiting scroll shaft penetrating system will be described below.

A tip surface of a first fixing wrap having a spiral wall surface formed by a wall surface parallel to the central axis of the cylinder having a uniform height is coplanar with an end surface of the cylinder, and a spiral groove portion is opened; The opposite surface of the cylinder had a spiral shape in which the fixed scroll provided with the end plate forming the bottom surface of the spiral groove and the spiral shape matched to the tip end surface of the first fixed wrap, that is, a mirror image relationship with each other. The end plate of the fixed scroll having the second fixed wrap is composed of a circular shaft through hole provided in the center of a partition plate integrally formed with the back faces thereof and a discharge hole opened from the hole toward the outer periphery. In contrast to the fixed scroll with both teeth, a uniform height is formed on one side of the end plate, where a bulb-shaped bearing boss with a constant width on the outside and a shaft through hole in the center is formed by a spiral wall. Straightening swivel wrap The first orbiting scroll provided and the second orbiting scroll provided with the orbiting wrap in a mirror image relationship therewith are engaged with the first fixed wrap and the second fixed wrap so as to be fitted respectively to the first compression chamber 1. And a second compression chamber 2 and a shaft for driving the orbiting scroll through each shaft through-hole, and a rotation preventing mechanism provided on the back side of each orbiting scroll end plate, to constitute two sets of compression mechanism units.

[0011] In the shaft through holes of the first and second orbiting scrolls, orbiting bearings for directly supporting the centrifugal force and gas compression load of the orbiting scroll are mounted. The width of the bearing supporting the load is set substantially equal to the distance between the center point of the height of the orbiting wrap forming the compression chamber and the center of gravity of the orbiting scroll.

Next, looking at the relationship between the center of the spiral and the axis of the shaft through hole of the orbiting scroll in the case where an involute curve is used as the spiral curve, the outer wall of the bulb-shaped boss which is a part of the orbiting wrap has an involute curve. Formed,
The axis of the shaft through hole provided at the center of the boss is eccentric with respect to the center of the base circle of the involute curve, and the amount of eccentricity is from half the turning radius to half the value obtained by adding the lap tooth thickness to the turning radius. Is set.

A shaft for transmitting the power of the motor to the orbiting scroll via the orbiting bearing is passed through the shaft through-holes of the fixed scroll with double teeth and the shaft through-holes provided in the two orbiting scrolls, and the first near the power source. The shaft is supported by a main bearing provided at the center of the frame and an auxiliary bearing provided at the center of the second frame.

With respect to the rotation center of the shaft connecting the main shaft and the sub shaft of the shaft supported by the main bearing and the sub bearing, respectively, the amount of eccentricity of the center of the spiral of the fixed scroll and the orbiting scroll, that is, the turning radius The first orbital shaft on the main shaft side and the second orbital shaft near the countershaft inserted into the orbiting bearings of the two orbiting scrolls which are eccentric by the amount protruded vertically or forward and backward with the eccentric directions facing each other by 180 °. By using the shaft having the shape, the respective orbiting scrolls are driven at positions relatively opposed by 180 °.

The minimum length and shape of each of the connecting portion A provided between the first orbiting shaft and the second orbiting shaft and the connecting portion B provided between the auxiliary bearing and the second orbiting shaft are two orbiting scrolls. In the fixed position of the shaft. That is, the minimum length of the connecting portion A is more than twice the width of the slewing bearing, and that of the connecting portion B is formed to be slightly more than one times the width of the slewing bearing. Furthermore, the thickness of the central constricted portion of the connecting portion A, which has the lowest rigidity in the entire shaft, is determined by the overall shape of the connecting portion A so as to secure necessary strength and to enable the incorporation of the orbiting scroll during assembly. Can be The shape of the connecting portion B is similarly determined so that the strength and the orbiting scroll can be incorporated.

A plurality of pin crank mechanisms or Oldham mechanisms having a reciprocating sliding surface are provided between the respective frames having the main bearings and the sub bearings and the rear sides of the corresponding orbiting scroll end plates. Each of the rotation preventing mechanisms is mounted one by one. A part of the anti-rotation mechanism is arranged so as to hang on the rear side of the end plate of the revolving wrap forming the compression chamber, thereby achieving miniaturization.

Further, there is provided a balancer which balances the centrifugal force in the opposite direction caused by the center of gravity of the mass obtained by adding the orbit axis to the two orbiting scrolls being eccentric with respect to the center of rotation of the shaft and being phase-inverted by 180 °. Each of the balancers is provided on the shaft at a position outwardly distant from the main shaft or the countershaft, and the distance between the center of gravity of each balancer and the center of action of the centrifugal force acting on the rotating shaft close to each balancer is equal. So that the balancer shapes match each other.

During operation of the compressor, the outer peripheral portion of the orbiting scroll becomes a low-pressure space, and a high-pressure space is formed in the shaft through hole in the center of the partition plate of the fixed scroll with both teeth from which compressed gas is discharged. The compressed gas discharged into the high-pressure space is directly discharged to the outside from a discharge hole provided in the partition plate, or provided on a second frame having a sub-bearing through a discharge passage provided in a fixed scroll outer wall. After flowing into the high pressure chamber, it is discharged from the discharge pipe to the outside.

However, in the above-described configuration in which the shaft passes through the orbiting scroll, a mechanism for blocking and sealing the high-pressure space in the partition plate and the low-pressure space in the outer peripheral portion of the orbiting scroll is required. As a suitable means, there is a method in which a shaft seal is mounted at a position adjacent to the orbiting bearing on the tip side of the orbiting wrap of each of the two orbiting scrolls to make the inside of the orbiting bearing a low-pressure space. As a means suitable for another oil lubrication structure, a ring seal is provided between the back side of the two orbiting scroll end plates and each of the first frame and the second frame close to them, so that the inside of the orbiting bearing becomes a high-pressure space. There is a way.

As a method of reducing the gap between the wrap ends of the orbiting scroll and the fixed scroll to seal the space between the compression chambers, there is a means for attaching a tip seal to the end of the wrap, and a high or low pressure is provided on the back side of the end plate of the orbiting scroll. There is a method of pressing each orbiting scroll to the fixed scroll side by applying an intermediate enemy pressure of high pressure and high pressure.

The operation based on the technical means of the present invention is as follows.

The compressed gas can be easily discharged by the gas passage provided by using the thick portion for fixing the frame inside and around the partition plate separating the compression chamber of the fixed scroll with double teeth. In addition, by shifting the timing of the timing that flows into the first and second compression mechanisms and is compressed and discharged by 180 ° out of phase, the gas flow velocity is averaged, pressure pulsation is reduced, and pressure loss is also reduced.

The two pivots provided on the shaft are mutually
Since they face each other by 80 °, the gas compression load and the centrifugal force mainly generated by the orbiting scroll generated by the two sets of compression mechanisms acting on the orbiting axis are opposite to each other and are canceled out. However, since the moment associated with these loads remains, a small load receiving the moment associated with the gas load acts on the main bearing and sub-bearing, and the moment associated with centrifugal force is reduced by a small balancer provided near the main bearing and sub-bearing. Can be eliminated.

Although the fixed scroll with double teeth may be integrated, a control valve such as a discharge bypass valve is mounted in a space provided on a surface obtained by dividing the compression chamber into two in parallel with the bottom surface of the spiral groove. Thereby, the characteristics of the compressor are improved.

When a rolling bearing is used for the orbiting bearing or the main shaft, and a pin crank mechanism using a rolling bearing is applied as a rotation preventing mechanism, the shaft is located at a position adjacent to the tip of the orbiting wrap of the orbiting bearing in the central boss of the orbiting scroll at the same time. By mounting the seals at two locations to separate the high and low pressure space, an oil-free mechanism in which the shaft excluding the portion exposed to the discharge space is placed in the low pressure space can be easily achieved. Alternatively, if a sliding bearing is used for the orbiting bearing or main shaft, and an Oldham mechanism with a reciprocating sliding surface is applied as a rotation preventing mechanism, a ring seal mechanism is installed between the back of the orbiting scroll end plate and the frame to achieve high and low pressure. By separating the space, an oil lubrication structure in which the entire shaft is placed in the high-pressure space can be easily obtained.

Another invention for expanding the capacity by further adding a plurality of two sets of compression mechanism units using the fixed scroll with double teeth is conceivable.

As another invention, a shaft seal having a concentric axis with respect to the main shaft and the sub shaft is provided between the inside of the fixed scroll shaft through hole and the shaft, and at the same time, the fixed scroll and the orbiting scroll of the first compression mechanism are provided. The volume of the minimum sealed space formed between the spiral grooves and the volume of the maximum sealed space formed between the spiral grooves of the second compression mechanism are configured to be equal, and then the minimum sealed space and the maximum sealed space are formed. By providing a passage communicating with the space, a two-stage compression mechanism can be easily realized.

[0028]

DESCRIPTION OF THE PREFERRED EMBODIMENTS One embodiment of the present invention will be described below with reference to FIGS.

FIG. 1 is a sectional view of a multi-link scroll compressor applied to an oil-free mechanism according to an embodiment of the present invention. Two adjacent sets of compression mechanisms provided so as to be sandwiched between the first frame 11 and the second frame 12 arranged at the left end are shown in the section shown in the cross section. A motor that is directly connected to the shaft 6 that penetrates two sets of compression mechanisms is housed in a part that is hidden behind a case 16 fixed to the shaft 16.

Also, as shown in FIG. 2, two spiral fixed grooves 3b and 3d provided at the center with the same width and depth inward from both end surfaces of the cylinder toward the center of each other at the center. The first fixed groove 3b on the right side of the fixed scroll 3 having both teeth provided with a circular shaft through hole 3f approximately at the center of the plate 3a.
In addition, at the center of one side of the circular end plate 4a, the contour of the outer wall is formed from a bulb-shaped bearing boss 4c having a spiral curve. The orbiting wrap 4 of the first orbiting scroll 4 having a shaft through-hole 4d penetrating an end plate 4a opened approximately in the center of the bearing boss 4c and provided with the wrap 4b standing upright.
b, the first compression chamber 1 is formed, and in addition to these, three crankshafts 1 provided between the orbiting scroll end plate 4a and the first frame as shown in FIG.
5 having a first anti-rotation mechanism 13 and a shaft 6 having an eccentric pivot axis penetrating approximately in the center of the drawing.
Constitute a first compression mechanism.

As shown in FIG. 3, a revolving wrap 5b of a second revolving scroll 5, which is a mirror image of the first revolving scroll 4, is provided in a second fixing groove 3d provided on the left side of the fixed scroll 3 having both teeth. The second compression chamber 2 is formed by meshing with the second rotation preventing mechanism 14 including three crankshafts 15 provided between the orbiting scroll end plate 5a and the second frame. A second compression mechanism is constituted by a shaft 6 having an eccentric pivot axis which penetrates the center of the drawing laterally.

The spiral forming the first compression chamber 1 and the second compression chamber 2 is formed in an asymmetrical wrap shape, but may be formed in a symmetrical wrap shape, and the winding direction is the second as shown in FIGS. Both are formed in the same counterclockwise direction when viewed from the frame 12 side, and when viewed from the side where the spiral groove is opened, the winding directions are reversed and mirror images of each other. Accordingly, when the centers of the spirals are viewed together in one direction, the winding start position and the winding end position of the spiral of the first compression chamber 1 and the second compression chamber 2 are formed to be the same and overlap with each other, and The discharge position of the compressed gas is the same. Correspondingly, a communication passage 3i communicating the first compression chamber 1 and the second compression chamber 2 is provided at a suction position of the fixed scroll partition plate 3a, and a shaft through hole 3g is provided at a discharge position at the center of the partition plate 3a. Thus, a discharge space 30 is formed.

A communication passage 3i for communicating the suction side of the first compression chamber 1 and the suction side of the second compression chamber 2 is provided outside the fixed groove 3 at the end of the fixed groove. A discharge hole 3g opening to a discharge space 30 provided at the center of the plate and a discharge passage 3h connected to the discharge hole 3g are provided, and discharge is performed from a discharge passage 12c provided in the second frame to a high-pressure chamber 31 provided at the left end in FIG. After that, it is taken out of the discharge pipe 18.

The bearing boss 4 in the form of a bulb of the orbiting scroll
The detailed shape of c will be described with reference to FIG. The contours of the turning wrap 4b and the bearing boss 4c are formed from an involute curve, and a point (P) on the outer wall of the bearing boss represents a start position of the involute curve. Point ▲ P
The semicircular wall surface formed on the left of ▼ is shown as an envelope with respect to the leading end wall surface at the beginning of winding of the first fixed wrap 3c, and when the leading end wall surface has a semicircular shape whose diameter is the lap tooth thickness. The diameter of the semicircular arc shape starting from the point (P) on the orbiting scroll side is set equal to a value obtained by adding the lap tooth thickness to twice the orbiting radius. In the drawing, Oa representing the center point of the + mark represents the center of the base circle of the involute curve, and Ob represents the center point of the shaft through hole 4d and the slewing bearing 4e.
Then, the relative coordinates of Ob with respect to Oa are represented by a point {P}.
And the point which went outside π radian half way around from this ▲ Q ▼
If the first tip seal 22 is provided up to the vicinity of the point Q, the intermediate point between the point closest to the point Q and the point P is set. Is done.

A rolling bearing is used for the orbiting bearing 4e shown in FIG. 7, but the contact length with the surface of the orbiting shaft, that is, the bearing width Lb is determined by the center of gravity of the orbiting scroll and the center position in the height direction of the orbiting wrap. It is preferable that Lb be longer than this distance by about 10% to 20%, and the orbit bearing 5e of the second orbiting scroll is similarly configured. When these slewing bearings are composed of a plurality of ball bearings, the L
b corresponds to the distance between the centers of the ball bearings arranged at both ends.
Further, a shaft seal 7 that partitions a space on the back side of the end plate 3a that communicates with the low-pressure space with the front end of the first turning wrap communicating with the discharge space 30 of the shaft through hole 4d is provided at the front end of the first turning wrap of the first turning bearing 4e. It is provided on the side. In the shaft through hole 5d of the second orbiting scroll, a shaft seal that similarly partitions the high / low pressure space is provided on the discharge space side of the second orbiting bearing 5e.

In FIG. 14, which is a plan view of the fixed scroll, which is a plan view of the central part, FIG. 14 shows the center point of + mark, Oa indicates the center of the base circle of the involute curve, and Ob indicates the shaft through hole 3f.
Represents the center. The position of Ob substantially coincides with the rotation center of the shaft, that is, the line connecting the axes of the main bearing 11a and the sub-bearing 12a, and the diameter of the shaft through hole is obtained by adding twice the turning radius to the turning shaft diameter. Is set equal to or slightly greater than

First pivot 6 provided on shaft 6 in FIG.
a and the second turning shaft 6b are both eccentric with respect to the axes of the main shaft 6c and the sub shaft 6d by the turning radius, and
It is arranged at a position facing 0 °. These revolving shafts are inserted into a revolving bearing 4e mounted in a shaft through hole 4d of the first orbiting scroll and a revolving bearing 5e mounted in a shaft through hole 5d of the second orbiting scroll. A connecting portion A6e is provided between the first turning shaft 6a and the second turning shaft 6b.
A connecting portion B6f is provided between the second turning shaft 6b and the sub-shaft 6d. The shape of the two connecting portions is designed to secure the strength required to support the load applied to the shaft. It is determined by a method of incorporating the orbiting scroll 4 and the second orbiting scroll 5 to a predetermined position. The lengths l1 and l2 of the connecting portion A in the figure are both the orbiting bearings 4 of the first orbiting scroll.
e is approximately equal to the length obtained by adding the width of the shaft seal 7, and the length 13 of the second swing shaft 6b is approximately equal to the length obtained by adding the width of the shaft seal 7 to the swing bearing 5e. Then, the length l4 of the connecting portion B is adjusted to the longer one of l1 and l3.

As shown in FIG. 19, which models the shaft system on which the inertial force of FIG. 1 acts, the centrifugal force W2 of the first orbiting scroll 4 and the first orbiting shaft 6a acting on the first orbiting shaft of the shaft, and the second The centrifugal forces W1 of the second orbiting scroll 5 and the second orbiting shaft 6b acting on the orbiting shafts are opposite to each other and have substantially the same magnitude, so that the forces are balanced and canceled, but in order to eliminate the remaining rotational moment. Balancers having small centrifugal forces W3 and W4 as shown in the figure are arranged before and after the main bearing 11a and the sub-bearing 12a, respectively. And W3
The size of W4 and W4 need only be smaller as they are farther from W1 and W2.

The operation of the multi-link scroll compressor constructed as described above will be described below.

When the shaft 6 directly connected to the motor rotates, power is transmitted from the first orbiting shaft 6a and the first orbiting scroll 4 is driven.
The first orbiting scroll orbits or makes a revolving motion on a circular orbit by the rotation preventing mechanism composed of 5, and compresses after sucking gas from the outer periphery into the first compression chamber 1 formed between the first scroll and the fixed scroll 3. The liquid is discharged into the central discharge space 30. The second orbiting scroll 5 to which the power is transmitted from the second orbiting shaft 6b also functions similarly to the first orbiting scroll,
Orbiting motion and compression stroke are 180
° In order to be out of phase, the inflow of gas into the compression chamber and the outflow of gas into the discharge space are performed alternately from the first compression chamber 1 and the second compression chamber 2, and the suction side and the discharge side And the pressure pulsation is also small. The gas flowing into the discharge space flows into the high-pressure chamber 31 from the discharge holes and the discharge passage provided in the fixed scroll, passes through the discharge passage in the second frame, and flows out of the discharge pipe to the outside.

The independent configuration of the first orbiting scroll 4 and the second orbiting scroll 5 greatly increases the load on the orbiting bearing due to the gas compression load caused by the gas compression and the dispersion of the centrifugal force of the orbiting scroll. And the orbiting motion of the first compression chamber and the second compression chamber are 180 ° out of phase, so that the gas compression load accompanying the gas compression and the centrifugal force of the orbiting scroll are offset, and the main bearing 11a and the Bearing 1
The load on 2a can be greatly reduced.

Each of the first and second slewing bearings, the main bearing and the sub-bearing, and each of the three sets of three pin crank mechanisms are composed of rolling bearings. An oil-free mechanism is easily configured by partitioning the high / low pressure space by the shaft seal provided at the adjacent position.

Next, in the invention shown in FIG. 1, the fixed scroll is integrally formed. However, the center of the end plate shown in FIG. 9 is vertically divided to divide the fixed scroll into two, and a gas passage and a valve mechanism are provided on the end plate surface. It can be easily analogized that they can be integrally configured after mounting. It is also easy to analogize changing the spiral shape and the phase of the compression stroke of the second compression chamber of the first compression chamber. In this case, however, the amount of eccentricity of the second orbital axis is reduced by incorporating the first orbital scroll. Needs to be smaller than the amount of eccentricity.

Although the invention shown in FIG. 1 is shown on the premise of an oil-free mechanism, lubricating oil is sealed in a case and oil is supplied to each sliding portion formed of a sliding bearing to lubricate. In the case of, although not shown, the position of the partition of the high and low pressure space is moved between the end plate of the orbiting scroll and the frame by eliminating the shaft seal of FIG. This can be easily achieved by using the Oldham mechanism as the anti-rotation mechanism and pressing the orbiting scroll by the high pressure acting on the inside thereof.

Further, as an invention which can be easily analogized from the invention of FIG. 1, the volume of the minimum sealed space formed immediately before the discharge of the first compression chamber and the volume of the maximum sealed space immediately before the start of the compression stroke of the second compression chamber are the same. The two-stage compression mechanism is easily achieved by providing a shaft seal between the simultaneous shaft connecting portion A and the fixed scroll shaft through hole to completely separate the discharge space.

[0046]

In the multi-connection scroll compressor constructed as described above, by mounting a rotation preventing mechanism in the space provided on the back of the first and second orbiting scroll end plates, the size of the end plate of the orbiting scroll can be increased. Since the size is determined from the spiral shape excluding the anti-rotation mechanism, there is an effect that the compressor can be reduced in size and weight.

The two orbiting scrolls are made independent and at the same time are given a motion of 180 ° facing each other, so that the centrifugal force and gas compression load acting on the two orbiting bearings, the main bearing and the sub-bearing, and also on the anti-rotation mechanism. Can be dispersed and greatly reduced, thereby improving the durability of the bearing. Further, the gas compression loads generated in the first compression chamber and the second compression chamber are offset each other, so that there is an effect that the torque fluctuation is reduced and the vibration is reduced.

Further, the load acting on the main bearing and the sub-bearing can be greatly reduced, the seal gap between the compression chambers of the two independent orbiting scrolls can be optimized, and the rigidity can be fixed with high rigidity. By making the scroll side of both teeth, the processing accuracy of the spiral is improved, and there is an effect that the efficiency can be improved.

Further, the sub-shaft of the shaft is further extended to connect four or more sets of compression mechanism parts to increase the capacity, and the central discharge space of the fixed scroll with two teeth is divided into two parts to achieve two-stage compression. There is an effect that the mechanism can be easily configured.

[0050]

[Brief description of the drawings]

FIG. 1 is a sectional view of a scroll compressor according to the present invention.

FIG. 2 is a sectional view taken along line AA of FIG. 1;

FIG. 3 is a sectional view taken along line BB of FIG. 1;

FIG. 4 is a sectional view taken along the line CC of FIG. 1;

FIG. 5 is a sectional view taken along the line DD of FIG. 1;

FIG. 6 is a plan view of a first orbiting scroll.

FIG. 7 is a sectional view taken along line AA of FIG. 6;

FIG. 8 is a side view of the first compression chamber of the fixed scroll with two teeth.

9 is a sectional view taken along line AA of FIG. 8;

FIG. 10 is a sectional view taken along line BB of FIG. 8;

FIG. 11 is a plan view of a second orbiting scroll.

FIG. 12 is a side view of a second compression chamber of the fixed scroll with double teeth.

FIG. 13 is a central enlarged view of FIG. 6;

FIG. 14 is a central enlarged view of FIG. 8;

FIG. 15 is a front view of a shaft.

FIG. 16 is a view taken in the direction of arrow A in FIG. 15;

17 is a sectional view taken along line BB of FIG.

18 is a sectional view taken along the line CC in FIG.

FIG. 19 is a model diagram of centrifugal force acting on a shaft.

[Explanation of symbols]

1 is a first compression chamber, 2 is a second compression chamber, 3 is a fixed scroll, 3a is a partition plate 3b is a first fixed groove, 3c is a first fixed wrap, 3d is a second fixed groove 3e is a second fixed wrap, 3f is a shaft through hole, 3g is a discharge hole, 4 is a first orbiting scroll, 4a is an end plate, 4b is a turning wrap, 4c is a bearing boss, 4d is a shaft through hole, 4e is a turning bearing, 5 is a second turning scroll, 5a Is an end plate 5b is a revolving wrap, 5c is a revolving boss 5d is a shaft through hole, 5e is a revolving bearing 6, a shaft, 6a is a first revolving shaft, 6b is a second revolving shaft,
6c is a main shaft, 6d is a sub shaft, 6e is a connecting portion A, 6f is a connecting portion B, 7 is a first shaft seal, 8 is a second shaft seal, 9 is a first balancer, 10 is a second balancer, 11 is a first frame, 11a is a main bearing, 12 is a second frame, 12a is a sub-bearing, 13 is a first anti-rotation mechanism, 14 is a second anti-rotation mechanism, 15 is a crankshaft, 30 is a discharge space, and 31 is a high-pressure chamber.

Claims (3)

[Claims] A fixed scroll having a spiral wall formed by a wall parallel to a central axis in a cylinder having a uniform end face width and having a groove open only at one end or an upright wrap provided on an end plate; Orbiting scrolls provided on one side of a circular end plate and provided with wraps formed by spiral projections having a uniform height and perpendicular to the end plate are engaged with each other to form a compression chamber, and the orbiting scroll is rotated by using a rotation preventing mechanism. In a scroll compressor that revolves on a circular orbit, (1) the direction of winding of the first fixed wrap and the spiral is reversed on the back surface of the end plate opposite to the cylinder with respect to the end surface of the first fixed wrap provided on the fixed scroll. A circular shaft through hole provided at the center of a partition plate in which two fixed end plates have a second fixed wrap and are formed integrally with the rear surfaces of end plates of the other fixed scrolls. And its A fixed scroll with double teeth composed of a discharge hole opened from the hole to the outer periphery. (2) An outer peripheral side of a projection having a spiral wall surface having a uniform height and perpendicular to the end plate provided on one surface of the circular end plate is formed by a first turning wrap having a constant width, and is formed on an inner peripheral side thereof. At least one or a plurality of slewing bearings are mounted on the inner wall of a shaft through hole passing through the bearing boss and the end plate and opening at both end surfaces at approximately the center of the bulb-shaped bearing boss to be formed. A first orbiting scroll in which a part of a rotation preventing mechanism is formed on a back surface behind an end plate provided with an orbiting wrap. (3) A second spiral wrap formed in such a manner that the spiral direction of the projection having a spiral wall surface of a uniform height and perpendicular to the end plate provided on one side of the circular end plate is opposite to that of the first turning wrap. A second orbiting scroll having the same shape and size as the first orbiting scroll, except that the orbiting wrap and the bulbous bearing boss are formed. (4) A first part in which a substantially circular outer peripheral part is fixed to one end of the fixed scroll, a main bearing is provided in a central part, and a part of a rotation preventing mechanism mounted between end plates of the first orbiting scroll is configured. flame. (5) An anti-rotation mechanism of which a substantially circular outer peripheral portion is fixed to an end surface of the fixed scroll opposite to the first frame, a sub-bearing is provided at a center portion, and the auxiliary anti-rotation mechanism is mounted between end plates of the second orbiting scroll. A second frame that is partially constructed. (6) a main shaft and a sub shaft which are inserted into the main bearing and the sub bearing, respectively, as a center of rotation; and the center of the shaft is eccentric by a turning radius with respect to the center of rotation, and each of the first and second orbiting scrolls is turned. A connecting portion A is provided between the first and second rotating shafts, and a connecting portion B is provided between the first and second rotating shafts and the counter shaft. A shaft provided with the first pivot axis and the second pivot axis disposed 180 ° opposite to each other, and one end of which is connected to a power source such as a motor; (7) At least a portion corresponding to the rear surface of a part of the orbiting wrap without penetrating the end plate on the opposite side of the orbiting wrap, that is, on the back side of the outer periphery of the first orbiting scroll end plate. A first anti-rotation mechanism for preventing rotation of the first orbiting scroll provided between one frame. (8) A second anti-rotation mechanism in which the same configuration as the first anti-rotation mechanism is provided between the rear surface of the second orbiting scroll end plate and the second frame. A multi-link scroll compressor characterized by having the above configuration. (1) A fixed scroll with double teeth, in which a tip seal is attached to the tip of a spiral wrap. (2) A tip seal is attached to the tip of the spiral wrap, and a rolling bearing is used for the slewing bearing in the bearing boss.
Further, one end in the width direction of the orbiting bearing is disposed so as to be located approximately at the center of the orbiting wrap, and the other end is located at the center of gravity of the orbiting scroll, and a shaft seal is provided adjacent to the tip of the orbiting wrap of the orbiting bearing. First orbiting scroll and second orbiting scroll installed. (3) First and second frames using rolling bearings for the main bearing and auxiliary bearing. (4) The first orbiting scroll is provided with three pin-crank mechanisms which are connected by a crank shaft between a rolling bearing mounted on the back side of the end plate and a rolling bearing mounted on the first frame side. An anti-rotation mechanism and a second anti-rotation mechanism similarly provided with three pin crank mechanisms on the rear side of the second orbiting scroll. The multi-connection scroll compressor according to claim 1, which is suitable for an oil-free mechanism configured as described above. 3. The shape of the first fixed wrap and the second fixed wrap formed from both end surfaces of the cylinder overlap in one direction, and the pitch of the spiral curve is such that they are mirror images of each other when viewed from the front. , The tooth thickness and tooth height of the wrap and the winding angles at the beginning and end are respectively matched, and both the shafts are constituted by shaft through holes having a diameter approximately equal to the value obtained by adding twice the turning radius to the diameter of the first turning shaft. Fixed scroll with teeth. (2) Like the fixed scroll with both teeth, the first orbiting wrap and the second orbiting wrap have the same shape with their leading end surfaces matched so as to have a mirror image relationship, and the wrap heights are equal. A first orbiting scroll and a second orbiting scroll, wherein the center of the orbiting bearing is provided at a position shifted from the center of the spiral by a half of the turning radius plus the lap tooth thickness or by a half of the turning radius. (3) The diameter of the first pivot axis, the second pivot axis, the main axis, and the sub-axis are all equal, and have a connection portion A that is approximately twice as long as the connection portion B, and between the main axis and the first pivot axis and the sub-axis. A shaft in which a balancer of the same size is arranged between the first and second pivot axes. 2. The apparatus according to claim 1, wherein
Multi-connection scroll compressor.