JPH09317663A - Scroll compressor - Google Patents

Abstract

(57) [Abstract] [Problem] When performing a turning motion using an Oldham ring,
The key part of the Oldham ring is reciprocal sliding, and when the moving direction reverses, the sliding speed is always 0, and it becomes difficult to realize a good sliding form because it becomes a condition that the lubricating oil is likely to run out. An orbiting scroll (2b) driven by a driving force of an electric motor via a crankshaft (5) and an orbiting scroll (2).
b, a fixed scroll 2a that meshes with b to form a compression chamber that compresses the refrigerant gas, a bearing 3b that supports the rotational movement of the crankshaft 5 and that supports the orbiting scroll 2b to orbit, and orbits the crankshaft 5. A radial direction cushioning portion that rotatably supports the scroll 2b and that can move only in a direction in which the turning radius of the turning motion becomes smaller,
By a link mechanism that connects the bearing 3b and the orbiting scroll 2b via one or more driven crankshafts 31 having an eccentric portion and the crankshaft 5, a rotation prevention mechanism portion 31 that maintains the angular positional relationship of the orbiting scroll 2b with respect to the bearing 3b. A scroll compressor characterized by having.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a scroll compressor used for refrigeration and air conditioning. In particular, the present invention relates to a scroll compressor that is advantageous in terms of reliability and efficiency when using an HFC-based CFC refrigerant whose sliding conditions are stricter than conventional ones.

[0002]

2. Description of the Related Art Scroll type compressors are used in the fields of refrigeration and air conditioning for home and business use, taking advantage of their characteristics of low noise and low vibration. Here, this scroll compressor will be described as an example.

FIG. 9 shows a vertical sectional view of a conventional scroll compressor. At the upper part of the closed container 1, a fixed scroll 2a
And a compression mechanism 2 in which an orbiting scroll 2b that orbits with respect to the fixed scroll 2a is engaged, and an orbiting scroll 2
There is provided a bearing component 3 in which a thrust bearing 3a supporting b and a bearing 3b supporting the crankshaft 5 are integrated.

The shaft 2c of the orbiting scroll 2b is inserted into an eccentric bearing 6 having a substantially rectangular outer shape of a deformed hole 5b having a bottom surface provided on the upper end of the crankshaft 5. And
Rotation of the rotation preventing mechanism of the Oldham ring 20 and the crankshaft 5 causes the orbiting scroll 2b to orbit.

The eccentric bearing 6 is constructed so as to be movable in the direction of reducing the turning radius, and is elastically pressed in the turning radius direction by the coil spring 4 so as to keep the maximum turning radius e. The crankshaft 5 has a rotor 7a of the electric motor 7.
Are mounted below the bearing component 3 together with the stator 7b which is shrink-fitted and fixed to the closed container 1. The crankshaft 5 includes a main bearing 8 and a sub bearing 2 of the bearing component 3.
It is supported by 3 and. A gas suction pipe 11 is provided on the side of the sealed container 1. The gas pressure on the suction side is below the spacer 22 inside the closed container 1,
A gas pressure on the compression side acts above the spacer 22.

If an abnormal force due to suction of dust or liquid refrigerant is applied during the compression operation, the dough 2a can be moved by contracting the coil spring 4 in the direction in which the turning radius e becomes smaller, By this movement, the abnormal pressure and force can be buffered.

Reference numeral 15 is a discharge chamber provided at the upper portion of the fixed scroll, and 16 is a discharge pipe for discharging compressed gas to the outside of the closed container 1. The fixed scroll 2a and the bearing component 3 are fastened with bolts (not shown) with the spacer 22 interposed therebetween. The spacer 22 is hermetically welded and fixed to the airtight container 1 at its outer periphery, and serves as a partition between a lower suction pressure portion and an upper compression pressure portion. Reference numeral 19 is a check valve for preventing the orbiting scroll 2b from reversing when stopped, 24 is a check valve guide for restricting the movement of the check valve, 2
0 is an Oldham ring for preventing rotation for rotating the movable scroll 2b with respect to the fixed scroll 2a, and 2
Reference numeral 1 is a suction port provided in a bearing component 3 for sucking low-pressure gas into the compression mechanism 2.

An oil sump 10 for storing the lubricating oil 9 is provided at the lower bottom of the closed container 1. The lubricating oil 9 is sucked up from an oil guide 14 at the lower end of the crankshaft 5 and provided on the crankshaft 5. Through the through hole 13, each bearing portion, that is, the main bearing 8, the auxiliary bearing 23, the eccentric bearing 6, the thrust bearing 3
lubricate a and cool the bearing members,
After that, the oil is discharged from the oil discharge port 12 provided in the bearing component 3 and discharged to the upper portion of the stator 7b, and returns to the oil sump 10 through the cutout portion 18 of the stator 7b.

Next, the operation of the compression mechanism having the above structure will be described. The low-pressure gas returns from the suction pipe 11 and is sucked into the compression mechanism 2. When the orbiting scroll 2b orbits with respect to the fixed scroll 2a, the sucked gas becomes a high-pressure gas compressed by the compression mechanism 2, and once enters the discharge chamber 15. Then, the gas is discharged from the discharge pipe 16 to the outside of the closed vessel 1 and the low-pressure gas is circulated again, thereby forming a known compression cycle.

The state of the turning motion will be described with reference to FIG. FIG. 10 is a cross-sectional view taken along line RR shown in FIG. 9 and viewed from the direction of the arrow.

In FIG. 10, Os is the center of the XY coordinates and the center of the fixed scroll 2b, and Oo is the center of the orbiting scroll. The point Oo turns clockwise on a turning circle having a turning radius e centered on the point Os. The starting point of the turning motion is set to a state where there is a point Oo on the X axis, and the turning angle, that is, the crank angle θ is taken. FIG. 10A shows a state of θ = 0, and FIGS. 10B, 10C, and 10D show a state in which the crankshaft 5 is rotated by 90 °.

An Ordham ring 20 (not shown in FIG. 10) conventionally used as a rotation preventing mechanism causes the orbiting scroll 2a to move on the orbiting circle, but it is XY.
The orbiting scroll 2a does not rotate with respect to the coordinates.
It can be understood by looking at the movement diagrams 10 (a) to 10 (d).

To explain the state of compression in this swirling motion, in FIG. 10 (a), a pair of symmetrical compression chambers (shown by A and B), which are substantially outermost chambers, are formed and suction of low pressure gas is performed. Has been completed. The low-pressure gas thus sucked moves to the center while being compressed as the volumes of chambers A and B decrease as the crankshaft 5 rotates. On the way,
Chambers A and B communicate with one another in chamber C at the center (θ in FIG. 10).
= Communication about 45 °), and then, during one further rotation, is discharged into the discharge chamber 15 as high-pressure gas from the discharge port 25 of the chamber C.

[0014]

H which is the next alternative refrigerant
Since FC type CFC refrigerants cannot be expected to have a lubricating effect due to the extreme pressure action of chlorine, which is said to exist in CFC type and HCFC type refrigerants, the reliability and efficiency of scroll compressors and the like when HFC type CFC refrigerants are used. In order to make the value high, it is necessary to further consider from the viewpoint of lubrication and sliding. In the lubrication and sliding, it is necessary to consider the load reduction, the sufficient supply of lubricating oil, and the like.

However, when the Oldham ring is used to perform the turning motion, the key portion of the Oldham ring is reciprocal slide, and the sliding speed is always 0 when the moving direction is reversed.
It is difficult to say that this is a good sliding form because the conditions are such that the lubricating oil will run out easily. In fact, I am worried about reliability.

An object of the present invention is to solve the problems of such a conventional scroll compressor, and to provide a scroll compressor having high reliability and efficiency even when an HFC-based CFC refrigerant is used.

[0017]

In order to achieve the above object, the invention according to claim 1 of the present application provides an orbiting scroll driven by a driving force of an electric motor via a crankshaft, and a refrigerant gas meshing with the orbiting scroll. A fixed scroll that forms a compression chamber that compresses, a bearing that supports the rotational movement of the crankshaft and that supports the orbiting movement by mounting the orbiting scroll, and the orbiting that rotationally supports the orbiting scroll with respect to the crankshaft. A radial buffering portion that is movable only in a direction in which the orbiting radius of movement is reduced, one or more driven crankshafts having an eccentric portion, and a link that connects and forms the bearing and the orbiting scroll via the crankshaft. A rotation prevention mechanism section that maintains an angular positional relationship of the orbiting scroll with respect to the bearing by a mechanism. A scroll compressor according to claim.

Further, the invention according to claim 2 of the present application includes an orbiting scroll which is driven by a driving force of an electric motor through a crankshaft, and a fixed scroll which meshes with the orbiting scroll and forms a compression chamber for compressing a refrigerant gas. A bearing that supports the rotational movement of the crankshaft and supports the orbiting scroll by mounting the orbiting scroll, and only in a direction that rotationally supports the orbiting scroll with respect to the crankshaft and reduces the orbiting radius of the orbiting movement. By a link mechanism that connects the bearing and the orbiting scroll via the crankshaft having one or more driven crankshafts having an eccentric portion and a movable radial buffering portion, and the orbiting scroll, the orbiting scroll of the orbiting scroll with respect to the bearing is formed. It has a rotation prevention mechanism that keeps the angular position, and maximum torque is generated on the crankshaft. Approximately 90 ° delayed on angle to the crank angle, a scroll compressor, wherein a driven crank shaft center of the side that is fixed to the bearing is installed.

Further, the invention according to claim 3 of the present application includes an orbiting scroll which is driven by a driving force of an electric motor through a crankshaft, and a fixed scroll which meshes with the orbiting scroll to form a compression chamber for compressing a refrigerant gas. A bearing that supports the rotational movement of the crankshaft and supports the orbiting scroll by mounting the orbiting scroll, and only in a direction that rotationally supports the orbiting scroll with respect to the crankshaft and reduces the orbiting radius of the orbiting movement. By a link mechanism that connects the bearing and the orbiting scroll via the crankshaft having one or more driven crankshafts having an eccentric portion and a movable radial buffering portion, and the orbiting scroll, the orbiting scroll of the orbiting scroll with respect to the bearing is formed. It has a rotation prevention mechanism that keeps the angular position, and supplies lubricating oil to the driven crankshaft. Through hole, a scroll compressor, characterized in that formed in the axial direction of at least one said driven crankshaft.

Further, according to a fourth aspect of the present invention, there is provided an orbiting scroll driven by a driving force of an electric motor via a crankshaft, and a fixed scroll which meshes with the orbiting scroll to form a compression chamber for compressing a refrigerant gas. A bearing that supports the rotational movement of the crankshaft and supports the orbiting scroll by mounting the orbiting scroll, and only in a direction that rotationally supports the orbiting scroll with respect to the crankshaft and reduces the orbiting radius of the orbiting movement. By a link mechanism that connects the bearing and the orbiting scroll via the crankshaft having one or more driven crankshafts having an eccentric portion and a movable radial buffering portion, and the orbiting scroll, the orbiting scroll of the orbiting scroll with respect to the bearing is formed. The driven crankshaft has a rotation preventing mechanism that maintains an angular positional relationship. Or a scroll compressor, wherein it is formed by a bearing with different materials main component.

[0021]

BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of the present invention will be described below with reference to the drawings. The vertical cross-sectional view of the scroll compressor of the conventional example shown in FIG. 9 is almost the same as the compression mechanism portion except the bearing and its peripheral portion. Therefore, the same functional parts are designated by the same reference numerals, and detailed description thereof will be omitted. Omit it.

First, a first embodiment of the present invention will be described with reference to FIGS. 1 is a longitudinal sectional view of a main part of the present embodiment, FIG. 2 is a perspective explanatory view of main parts of the present invention,
FIG. 3 is a cross-sectional view of the main part.

In FIG. 1, the compression mechanism 2 in which the orbiting scroll 2b that orbits with respect to the fixed scroll 2a is engaged.
2 shows a thrust bearing 3a supporting the orbiting scroll 2b, a bearing component 3 integrated with a bearing 3b supporting the crankshaft 5, and a driven crankshaft 31. The orbiting scroll shaft 2c is inserted into an eccentric bearing 6 having a substantially rectangular outer shape in a deformed hole 5b provided at the end of the crankshaft 5, and the center axis Os of the crankshaft 5 and the center of the scroll shaft 2c are inserted. Axis O
O is separated by a distance e corresponding to the turning radius due to the eccentric bearing. The eccentric bearing 6 is configured to be movable in the direction of reducing the turning radius, and is further urged by the coil spring 4 which is an elastic body so as to maintain the maximum turning radius e.

Reference numeral 31 is a driven crankshaft which serves as a rotation preventing mechanism, and includes a fixed side shaft 31a and a turning side shaft 3 which are separated by an inter-axis distance e.
1b (see FIG. 2), the holes into which the respective shafts are inserted are fixed holes 32 of the thrust bearing 3a and the orbiting side hole 3 on the side facing the thrust bearing 3a of the orbiting scroll 2b.
It is installed as 3.

FIG. 2 is a schematic diagram of the driven crankshaft 31.
The center axis O1 of the fixed side shaft 31a and the turn side central axis O2 of the turning side shaft 31b are eccentric by the turning radius e. The driven crank shaft 31 is installed between the rotating roll 2b and the thrust bearing 3a. 37 is a lubricating oil supply path hole,
It is provided so as to coincide with the central axis of rotation O2, and the lubricating oil is pushed up and supplied by the centrifugal force generated as the shaft rotates. Predetermined clearances are secured in the fixed-side and swivel-side shafts 31a and 31b and the holes 32 and 33 into which they are inserted so that normal rotational sliding can be performed between the shaft holes.

The flow of lubricating oil on the driven crankshaft 31 will be described with reference to FIG. The lubricating oil 9 coming up through the through hole 13 of the crankshaft 5 is deformed into the deformed hole portion 5b and the eccentric bearing 6
And a scroll shaft 2c, and a space Vc formed between the tip of the crankshaft 5 and the bearing 3 passes through the gap between the bearing 3b and the crankshaft.
4), thrust bearing 3a and orbiting scroll 2b.
Flows in between.

After that, a part of the lubricating oil mainly flowing from the space Vc to the thrust bearing side through the passage 34 provided in the fixed side hole 32 from the inner diameter portion of the thrust bearing 3a is transferred to the fixed side hole 32 and the fixed side shaft 31. It is made to flow into a gap formed between the side surface and the bottom Mb surface (see FIG. 2), and further between the back surface of the orbiting scroll 2b and the Ma surface (see FIG. 2) of the driven crankshaft.

Further, the lubricating oil 9 flowing to the sliding portion of the fixed side hole 32 and the bottom Mb surface of the fixed side shaft 31 flows out from the discharge port 36 provided at the bottom of the fixed side hole 32 and the driven crankshaft. The oil supply passage hole 37 of 31 goes up to flow into a gap 38 provided between the Mc surface on the driven crankshaft 31 and the turning side hole 33. Further, from the gap 38 to the turning side shaft 31b
There are two types, one that flows through the gap between the side surface of the fixed side hole 33 and the fixed side hole 33 and that flows to the gap 35, and the other that passes through the gap 38 and passes through the inside of the orbiting scroll to the outside through a through hole 39 provided outside.

As described above, the through hole 1 of the crankshaft 5 is always provided.
By providing a path for the lubricating oil 9 to flow from 3 to the sliding portion of the driven scroll 31, lubrication can be more reliably performed, efficiency is improved by reducing sliding loss, and the cooling effect of the lubricating oil is added to increase reliability. become.

Needless to say, the same effect can be expected without using the oil supply passage hole 37 provided in the driven crankshaft 5 if the oil supply flow rate from the passage 34 is sufficient. However, when the oil supply flow rate is small, it is considered that lubrication of the orbiting-side shaft 31b becomes stricter first, so that it is effective to install the oil supply passage hole 37 capable of supplying oil by utilizing centrifugal force.

Next, referring to FIGS. 4 and 5, the driven crankshaft 3
The turning motion according to 1 will be described. FIG. 4 is a sectional view taken along the line P shown in FIG. 1 and viewed in the direction of the arrow.

The XY coordinates are the same fixed scroll as in FIG.
Are the coordinates of. The figure shows a swivel disc that swivels in the direction of arrow Q.
The center Oo of the roll is on the Y-axis (Y-axis direction rather than X-axis direction)
The crank angle .theta. = 90.degree. Obedience
Fixed side central axis O of the dynamic crankshaft 31₁Fixed side to support
From the center Os of the thrust bearing 3a to Os-O ₁
Distance r₁And the angle θ from the X axis₁At the position of
Revolving side central axis O_TwoThe turning side hole 33 that supports the
From the center Oo of the back surface of the roll 2b to Oo-O_TwoIndicated by
Same distance r as above₁And the angle θ from the X axis₁Is provided at the position
You. This Os-Oo-O_Two-O₁With 4 parallel link mechanism
Has formed.

Since the line shown between Os and O ₁ is the fixed arm 41 integral with the thrust bearing and of course does not move, the drive arm 42 shown between Os and Oo swings around the central axis Os. When the driven arm 43 shown by O ₁ -O ₂ rotates in the Q direction on the orbiting circle 45a of E, the driven arm 43 rotates around O ₁ in the Q direction on the orbiting circle 45b of the orbiting radius e.
The connecting arm 44, which is integral with the orbiting scroll shown between o and O ₁ , does not rotate but only moves in parallel. FIG.
(A) to (h) show the swing motion of OoO ₁ corresponding to the connecting arm from the crank angle θ = 0 ° to one rotation. The drive arm 42 is connected to the connecting arm 4 by θm in FIG.
It is a crank angle that is perpendicular to 4.

By the way, when the arms are overlapped as shown in FIGS. 5 (d) and 5 (h), the driven arm 43 may rotate in the opposite direction to the Q direction depending on the balance of forces. Sex seems to be low. Such a possibility seems to be when a large force is applied to the driven arm 43 or the like in the states (d) and (h). Therefore, the installation position of the driven crankshaft 31 should be determined so as not to be in the above states (d) and (h) at the crank angle where the most force is applied during the rotation of the crankshaft.

When the most force is applied to the crankshaft, it is immediately before the A2 and B2 chambers in FIG. 6 become one C chamber. Therefore, the crank angle at this time is set to θe, and
Considering the states of (d) and (h), the crank angle θ = θ
At e, the angle β of the driven arm 42 of the driven crankshaft 31 and the fixed arm 41 should not be 0 ° or 180 °. Furthermore, it should be installed so that β is as close to 90 ° as possible. Naturally, depending on the conditions, if 0 ° <| β | ≦ 90 °, no problem may occur. Here, as shown in FIG. 7 (a), β = 90 °, that is, the driven crankshaft was installed at a position 90 ° ahead of the crank angle θe in the motor rotation direction, and good results could be obtained.

Further, in this configuration, the driven crankshaft 31
The fixed-side shaft 31a and the swivel-side shaft 31b rotate in the same direction as the crankshaft 5 in the inserted hole, which is a rotation sliding condition. Therefore, the oil film is also cut off compared to the conventional reciprocating sliding of the Oldham ring. It is difficult and can be improved in reliability and efficiency.

With the structure simpler than the conventional one as in the first embodiment, the rotation of the rotation preventing mechanism is rotationally slid, so that the efficiency and the reliability are improved. It is possible to provide a scroll compressor that can be realized at low cost.

Next, a second embodiment will be described with reference to FIG. This embodiment is different from the first embodiment in that
Further, the reliability can be improved.

That is, the installation position of the driven crank shaft 31 is
In particular, it is installed in a direction of -90 °, which is opposite to the rotation direction from the crank angle θe. According to this configuration, since the drive arm 41 rotates in the state of pulling the driven arm 42 near the crank angle at which the force is most applied, the drive arm 41 is rotated in a pushing state and is more susceptible to disturbance such as vibration than in the case of FIG. 7A. Can perform strong and smooth exercise. Therefore, the reliability and efficiency can be improved by an easy change.

Next, a third embodiment will be described with reference to FIG. The present embodiment realizes an improvement in reliability and a cost reduction equivalent to or higher than that of the driven crankshaft used in the first embodiment, by using a configuration different from that of the driven crankshaft.

In the configuration shown in FIG. 8A, the fixed side and turning side shafts 31a and 31b of FIG. 2 are provided with two pins 53 and an eccentric ring 5.
It is of a form divided into 1. Here, the pin 52 is fixed to the orbiting side hole 33 of the orbiting scroll 2b by interference fit, the pin 53 is inserted into the eccentric hole 52 of the eccentric ring, and the pin 53 is rotated in the eccentric hole 52. Therefore, the rotational sliding is performed on the outer peripheral surface of the eccentric ring 51 and the inner peripheral surface of the eccentric hole 52.

According to this structure, as compared with the form forming shown in FIG. 2, two body parts that can be prepared easily can be prepared, which is advantageous in terms of cost. Although the pin 51 is fixed to the turning hole 33, it goes without saying that the same effect can be obtained even if the pin 51 is not fixed to the turning hole or fixed to the eccentric hole 52 side.

Further, FIG. 8B shows another form. This is one in which two central axes O1 and O2 are provided in the Mc plane. According to this configuration, since the center holes 56 and 57 can be located on the Mc plane and the Mb plane on the central axis during machining, machining on a lathe or the like is facilitated, which is advantageous in terms of cost.

Next, a fourth embodiment will be described with reference to FIG. This embodiment has further improved reliability as compared with the first embodiment.

As the material of the driven crankshaft 31, the fixed side hole 3
2 and the material of which the main component is different from the material of the turning side hole 33. When the refrigerant used is an HFC type, the different materials have better lubricity. When iron-based castings are used for the fixed-side hole 32 and the turning-side hole 33, the driven crankshaft 31 made of a material containing aluminum as its main component is better than an iron-based material against wear and the like. It showed a good result. Therefore, with this configuration, it is possible to provide a scroll compressor having a reliability and efficiency equal to or higher than those of the first and second embodiments.

The coil spring 4 used in the above construction is
It may be a leaf spring, and is not limited to these as long as it has necessary elasticity, refrigerant resistance, and oil resistance.

Further, the driven crankshaft 31 shown in FIG.
The refueling passage hole 37 has a fixed central axis O. ₁On the C plane
If the position is the turning center axis O_TwoIt is the same even if it is not provided to match
It goes without saying that there is such an effect.

Further, as can be seen from FIG. 5, the same effect can be obtained even if a plurality of driven crankshafts are installed. However, in this case, it goes without saying that the cushioning mechanism in the radial direction of the crankshaft 5 becomes ineffective, so that reliability must be taken into consideration accordingly. The installation position is
As described above, it is preferable to determine that the largest force acts on the drive arm when the drive arm pulls the driven arm.

Further, the fixed-side and turning-side shaft diameters of the driven crankshaft are not limited to the above-mentioned examples, and both the same shaft diameter and a turning-side larger than the fixed side can be considered. However, in that case, it is necessary to consider the lubrication passages on each sliding surface.

[0050]

As is apparent from the above description, according to the present invention, it is possible to realize and provide a scroll compressor having higher reliability and efficiency than ever before. In particular, it is possible to realize and provide a scroll compressor having higher reliability and efficiency even for the HFC-based CFC refrigerant which is a candidate for the next alternative refrigerant.

[Brief description of drawings]

FIG. 1 is a longitudinal sectional view of a main part of a scroll compressor according to a first embodiment.

FIG. 2 is a perspective view of a component used in the first embodiment.

FIG. 3 is a vertical sectional view used for explaining a lubricating oil passage according to the first embodiment.

FIG. 4 is a transverse cross-sectional view of the first embodiment.

FIG. 5 is an operation explanatory diagram according to the first embodiment.

FIG. 6 is a cross-sectional view used to describe the first embodiment.

FIG. 7 is a cross-sectional view of another form of the second embodiment.

FIG. 8 is a perspective view of another component according to the third embodiment.

FIG. 9 is a vertical sectional view of a scroll compressor in a conventional example.

FIG. 10 is an operation explanatory diagram of a scroll compressor in a conventional example.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 closed container 2 compression mechanism 2a fixed scroll 2b orbiting scroll 3 bearing 4 coil spring 5 crankshaft 6 eccentric bearing 31 driven crankshaft 32 fixed side hole 33 orbiting side hole 34-39 lubricating oil passage, gap

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Fumitoshi Nishiwaki 1006 Kadoma, Kadoma City, Osaka Prefecture Matsushita Electric Industrial Co., Ltd. (72) Hideki Nakata 1006 Kadoma, Kadoma City, Osaka Matsushita Electric Industrial Co., Ltd. 72) Inventor Hiroshi Hasegawa, 1006 Kadoma, Kadoma, Osaka Prefecture, Matsushita Electric Industrial Co., Ltd.

Claims (6)

[Claims] 1. An orbiting scroll driven by a driving force of an electric motor via a crankshaft, a fixed scroll which meshes with the orbiting scroll and forms a compression chamber for compressing a refrigerant gas, and a rotational movement of the crankshaft. A bearing for supporting the orbiting motion by mounting the orbiting scroll together, and a radial direction buffering part for rotationally supporting the orbiting scroll with respect to the crankshaft and being movable only in a direction in which the orbiting radius of the orbiting motion becomes smaller, A rotation preventing mechanism section that maintains an angular positional relationship of the orbiting scroll with respect to the bearing by one or more driven crankshafts having an eccentric portion and a link mechanism that connects and forms the bearing and the orbiting scroll through the crankshaft. A scroll compressor having: 2. An orbiting scroll driven by a driving force of an electric motor through a crankshaft, a fixed scroll which meshes with the orbiting scroll to form a compression chamber for compressing a refrigerant gas, and a rotational movement of the crankshaft. A bearing for supporting the orbiting motion by mounting the orbiting scroll together, and a radial direction buffering part for rotationally supporting the orbiting scroll with respect to the crankshaft and being movable only in a direction in which the orbiting radius of the orbiting motion becomes smaller, A rotation preventing mechanism section that maintains an angular positional relationship of the orbiting scroll with respect to the bearing by one or more driven crankshafts having an eccentric portion and a link mechanism that connects and forms the bearing and the orbiting scroll through the crankshaft. And has a delay of about 90 ° with respect to the crank angle at which the maximum torque is generated on the crankshaft. A scroll compressor characterized in that a driven crankshaft center on a side fixed to the bearing is installed on an angle. 3. An orbiting scroll driven by a driving force of an electric motor via a crankshaft, a fixed scroll which meshes with the orbiting scroll to form a compression chamber for compressing a refrigerant gas, and a rotational movement of the crankshaft being supported. A bearing for supporting the orbiting motion by mounting the orbiting scroll together, and a radial direction buffering part for rotationally supporting the orbiting scroll with respect to the crankshaft and being movable only in a direction in which the orbiting radius of the orbiting motion becomes smaller, A rotation preventing mechanism section that maintains an angular positional relationship of the orbiting scroll with respect to the bearing by one or more driven crankshafts having an eccentric portion and a link mechanism that connects and forms the bearing and the orbiting scroll through the crankshaft. And at least one through hole for supplying lubricating oil to the driven crankshaft. A scroll compressor formed in the axial direction of the rank axis. 4. An orbiting scroll driven by a driving force of an electric motor through a crankshaft, a fixed scroll which meshes with the orbiting scroll to form a compression chamber for compressing a refrigerant gas, and a rotational movement of the crankshaft being supported. A bearing for supporting the orbiting motion by mounting the orbiting scroll together, and a radial direction buffering part for rotationally supporting the orbiting scroll with respect to the crankshaft and being movable only in a direction in which the orbiting radius of the orbiting motion becomes smaller, A rotation preventing mechanism section that maintains an angular positional relationship of the orbiting scroll with respect to the bearing by one or more driven crankshafts having an eccentric portion and a link mechanism that connects and forms the bearing and the orbiting scroll through the crankshaft. The driven crankshaft is made of a material whose main component is different from that of the fixed scroll or the bearing. A scroll compressor characterized by being formed. 5. The scroll compressor according to claim 4, wherein the material of the bearing and the orbiting scroll is a casting material containing iron as a main component, and the driven scroll is a material containing aluminum as a main component. 6. The scroll compressor according to claim 1, wherein the refrigerant gas is an HFC-based CFC.