JPH07259758A - Scroll type processor - Google Patents

Abstract

PURPOSE:To reduce incurring of a machine friction loss owing to a load in radial direction by a method wherein a lever member is supported in spherical contraposition by a fixed member centering around one point on the fixed member and a revolving scroll member is supported in spherical contraposition by the lever member, and the lever member is supported in such a manner that an axis for interconnecting the two centers of the two spherical contraposition forms a rotary axis. CONSTITUTION:A scroll type compressor comprises a fixed scroll member 1 having an end plate part 2a and a scroll lap part 2b erected thereon; and a revolving scroll member 2 having the end plate part 2a and the scroll lap part 2b erected thereon. A lever member 27 is supported in spherical contraposition centering around one point of a fixed member by the fixed member and the revolving scroll member 2 is supported in spherical contraposition by the lever member 27 centering around a point being a spherical contraposition center different from that of the fixed member. In a deviated position wherein an axis passing the spherical contraposition centers of the lever member 27 and the fixed member forms a rotary axis, the lever member 27 is rotatably supported in a way that an axis for interconnecting the two spherical contraposition centers forms a relative rotary axis.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a scroll type compressor, and more particularly to a scroll type compressor suitable for use in a refrigerating cycle of a refrigerator or an air conditioner.

[0002]

2. Description of the Related Art A conventional scroll compressor is, for example,
As described in JP-A-2-264181, a crankshaft directly driven by a motor is used to revolve the orbiting scroll member, and the crankpin portion of the crankshaft and the orbiting scroll member are used. In this structure, a radial load due to the pressure of the compressed gas that acts on the scroll wrap portion of the orbiting scroll member acts on the rotary sliding portion and the rotary sliding portion of the motor bearing.

[0003]

SUMMARY OF THE INVENTION In the above conventional technique,
First, a relatively large radial load is applied to a rotary sliding portion having a high sliding speed such as a crank pin portion and a bearing portion, which causes a large mechanical friction loss and reduces the efficiency of the compressor. In addition, there is a problem that the sliding condition becomes strict under severe operating conditions, wear and seizure occur, and reliability of the compressor deteriorates. Further, the gap between the wraps of the fixed scroll member and the orbiting scroll member varies depending on the accuracy of each scroll member and the accuracy of the eccentricity of the crank pin portion of the crankshaft, and cannot be adjusted at the assembly stage.

An object of the present invention is to reduce mechanical friction loss caused by radial load and reduce wear and seizure in each part of a drive mechanism for orbiting a revolving scroll member in a scroll type compressor. In addition, the gap between the wraps of the scroll members is made small to improve the performance.

[0005]

In order to achieve the above-mentioned object of the present invention, the present invention replaces a conventional crankshaft as a drive mechanism for giving an orbiting motion to an orbiting scroll member,
The lever member is supported by a fixed member in a spherical pair about a point on the fixed member, and the orbiting scroll member is supported by the lever member in a spherical pair about a point different from the spherical pair center of the fixed member. , The two spherical surfaces of the lever member at a position deviated from the rotation axis by a rotation member having a rotation axis that is perpendicular to the end plate portion of the fixed scroll member and passing through the spherical pair center of the lever member and the fixed member. A drive mechanism configured to be rotatably supported by using an axis connecting the pair centers as a relative rotation axis is adopted, and a rotation support portion of the lever member by the rotating member from a spherical pair support center by the fixing member of the lever member. Is greater than the distance from the spherical pair support center of the lever member by the fixing member to the spherical pair support center of the roller by the lever member, A structure in which the shaft portion of the member is rotatably supported via a spherical bush, the movement in the thrust direction is restricted by the end surface of the spherical bush, and the thrust direction position of the spherical bush support member that supports the spherical bush by a spherical pair is adjustable. And

[0006]

First, by the structure of the first half of the means for solving the above problems, the lever member has the spherical pair center of the fixed member constrained to one point on the fixed member, and the rotary support portion by the rotary member serves as the fixed scroll member. Revolution is performed with an axis line that is perpendicular to the end plate portion and that passes through the spherical pair center of the lever member and the fixing member as a rotation axis. Therefore, the spherical pair center between the lever member and the orbiting scroll member is also perpendicular to the end plate portion of the fixed scroll member, and revolves around the axis passing through the spherical pair center between the lever member and the fixed member as a rotation axis to revolve around the orbiting scroll member. Can give exercise.

A relatively large load from the orbiting scroll member due to the pressure of the compressed gas acts on the lever member on the spherical pair with the orbiting scroll member. Is supported by the rotating pair part. Assuming now that the spherical pair of the lever member and the orbiting scroll member is the load point, the spherical pair of the fixed member is the fulcrum, and the rotating pair of the rotating member is the force point, the fulcrum is relative to the distance from the fulcrum to the load point. Since the distance from the force point to the force point is large, the amount of load applied to the rotating pair part with the rotating member, which is the power point, is the amount of load applied to the spherical pair part with the orbiting scroll member, which is the load point, due to the principle of leverage. Becomes smaller than Further, this also reduces the magnitude of the load applied to the bearing portion that supports the rotation of the rotating member.

Of the orbiting scroll member, the fixed member, and the rotating member, which are members that exert a load on the lever member,
The fixed member naturally does not rotate, and the orbiting scroll member also does not rotate by an anti-rotation mechanism such as the Oldham ring mechanism, but only the rotating member is perpendicular to the end plate portion of the fixed scroll member and the spherical surface between the lever member and the fixed member. Since it rotates about the axis passing through the center of kinematics as a rotation axis, it rotates about its axis. By the way, the sum of the loads acting between the lever member and each of the fixed member and the orbiting scroll member, which do not rotate, is:
Since the load is sufficiently large compared to the load that acts between the rotating member that performs rotation and the lever member, the rotational resistance torque that prevents the lever member from rotating due to frictional force is the rotational drive that tries to rotate due to frictional force. The torque is greater than the torque, and the lever member does not rotate about its own. Therefore, the lever member swings and slides with respect to the fixed member and the orbiting scroll member so that the tilt angle of the lever member central axis with respect to the axis substantially perpendicular to the end plate portion of the fixed scroll member is one amplitude and the rotary member is rotated. Relative rotation sliding.

As a result of the above, in the drive mechanism which orbits the orbiting scroll member, the sliding portion between the lever member and the rotating member and the bearing portion of the rotating member are rotationally slid, so that the sliding speed is high. Sliding load is reduced, and sliding is large at the sliding part between the lever member and the fixed member and at the sliding part between the lever member and the orbiting scroll member, but sliding due to oscillating sliding. Since the speed is reduced, the total mechanical friction loss due to the radial load in these sliding parts is reduced, and sliding parts under particularly severe sliding conditions are eliminated, so that the efficiency of the compressor can be improved.

Further, according to this means, both the radial load and the thrust load of the rotary member are supported by the cylindrical inner peripheral surface and the planar end surface formed on the spherical bush supported by the spherical pair. If the perpendicularity between the cylindrical surface of the inner surface of the spherical bush and the flat surface of the end surface is guaranteed, neither of them can hit one side, which also improves the reliability.
Further, the spherical bush can be moved and adjusted in the thrust direction together with the spherical bush support member that supports the spherical bush, and the rotary member whose movement in the thrust direction is restricted with respect to the spherical bush can also be adjusted in the thrust direction. .
As a result, the rotation support portion of the lever member of the rotation member can adjust its position in the thrust direction,
The tilt angle of the lever member with respect to the axis of rotation of the rotary member can be adjusted, and the orbiting radius of the orbiting scroll member, which is supported by a pair of spherical members by a part of the lever member, can be adjusted. Therefore, the gap between the wraps of the scroll member can be finely adjusted, and the performance is improved.

[0011]

Embodiments of the present invention will be described below with reference to FIGS. FIG. 1 is a side sectional view showing a scroll type compressor of a first embodiment of the present invention, and FIG. 2 is an enlarged view of a bearing portion of a rotor portion of a compressor driving motor which is a rotating member in FIG.

In the embodiment of the present invention shown in FIGS. 1 and 2,
The fixed scroll member 1 is composed of an end plate portion 1a and a scroll wrap portion 1b. The orbiting scroll member 2 also includes an end plate portion 2a and a scroll wrap portion 2b, and the scroll wrap portion 2b and the scroll wrap portion 1 are provided.
The fixed scroll member 1 is disposed so as to face the fixed scroll member 1 so as to mesh with b. A first plate member 3 is fixed to the outer peripheral portion of the fixed scroll member 1 by bolts 4 so as to surround the orbiting scroll member 2. Further, an Oldham ring is provided between the orbiting scroll member 2 and the first plate member 3. 5 is incorporated. On the orbiting scroll member 2 side of the Oldham ring 5, a pair of key portions 5a arranged in a straight line is formed and inserted into a pair of key groove portions 2c formed on the orbiting scroll member. Oldham ring 5
On the side of the first plate member 3 is formed a pair of key portions (not shown) arranged in a straight line at right angles to the pair of key portions 5a, and a pair of key groove portions of the first plate member 3 ( (Not shown). The outer periphery of the first plate member 3 is fixed to the chamber 6, and in the chamber 6,
The stator portion 7 and the second plate member 8 of the compressor driving motor are fixed. The first plate member 3 and the second plate member 8 are respectively formed with boss portions 3a, 8a and cylindrical hole portions 3b, 8b at their central portions, and these hole portions 3b, 8b are coaxial with each other. It is located in.

The main rotor member 9 has a shaft portion 9a formed at the left end in FIG. 1, and a permanent magnet 10 fixed to the outer peripheral portion. The main rotor member 9 is further formed with a cavity 11 penetrating from the end surface of the shaft portion 9a to the right end surface in FIG. The sub-rotor member 12 has a shaft portion 12a formed at an end portion in the right direction in FIG. 1, and a hole portion 12b opening in an end surface in the left direction in FIG. Is formed to be deviated to. Hole 12
A spherical support member 13 having an outer peripheral cylindrical surface portion and an inner peripheral spherical surface portion is inserted in b, and a spherical bush 14 having an outer peripheral spherical surface portion, an inner peripheral cylindrical surface portion, and flat surface portions at both ends is supported by the spherical surface support member 13. The so-called spherical bearing. Further, the spherical support member 13 is fixed so that its movement in the axial direction is restricted by a nut 15 having a thread formed on the outer circumference. Main rotor member 9 and sub rotor member 12
Means that the shaft portions 9a, 12a are integrally coupled by a bolt 16 so that the shaft portions 9a, 12a are coaxial with each other to form a rotor portion 17 of a compressor driving motor. Rotor part 1
7, two shaft portions 9a and 12a are provided in the center portion of the hole portion 3b of the first plate member 3 and the second plate member 8, respectively, and the intermediate support member 18 and the spherical bush support member 1 are provided.
A spherical bush 20 supported via 9 is rotatably fitted in the spherical bush 20 to support the bearing in a double-supported state.

FIG. 2 shows details of the periphery of the spherical bush 20. Since the screw portion 8c is formed coaxially with the hole 8b of the second plate member 8, the screw portion 8c has a cylindrical surface portion and a male screw portion which are coaxial with each other on the outer circumference, and the outer peripheral portion of the intermediate support member 18 having the cylindrical hole portion on the inner circumference. The screw portion 18a is screwed in, and after adjusting the position in the thrust direction, it is fixed by the lock nut 19. The radial position of the intermediate support member 18 is restricted by inserting the outer peripheral cylindrical surface portion thereof into the hole 8b of the second plate 8. Further, a spherical bush support member 9 having a cylindrical outer peripheral surface and a spherical inner peripheral surface is inserted into the inner peripheral cylindrical surface of the intermediate support member 18, and is fixed by a nut 22 having a threaded portion on the outer periphery. The spherical bush 20 is spherically supported on the spherical inner peripheral surface of the spherical bush support member 19 to form a so-called spherical bearing.

Ring-shaped members 23, 24 made of a material having excellent sliding characteristics are in contact with both ends of the spherical bush 20, and the shaft portion 12a of the auxiliary rotor member 12 rotates through these three parts. It is possible to be inserted. A washer member 25 is fixed to the shaft portion 12a by a nut 26. The washer member 25 and the end face portion 12c of the sub rotor member 12 sandwich three parts with a minute gap, and the sub rotor member 12 thrusts against the spherical bush 20. It regulates the movement in the direction. Further, in the present embodiment, the spherical bush 20
The ring-shaped members 23, 24 are incorporated between the end surface portion 12c of the auxiliary rotor member 12 and the washer member 25 for the purpose of improving the sliding resistance, but they are omitted to reduce the number of parts, and the spherical surface is omitted. Bush 20 and sub rotor member 1
Alternatively, the second end surface portion 12c and the washer member 25 may be brought into direct contact with each other.

As a result of the above construction, by adjusting the thrust direction position of the intermediate support member 18, it is possible to finally adjust the thrust direction position of the rotor member 17.

The lever member 27 has a spherical portion 27a at one end,
A cylindrical surface portion 27b is formed at the other end, and another spherical surface portion 27c is formed between them, and the axis connecting the spherical center of the spherical surface portion 27a and the spherical center of the spherical surface portion 27c is the cylindrical surface portion 27b.
Has become the central axis of. The lever member 27 has a cylindrical surface portion 27.
A spherical surface b is rotatably fitted into the inner peripheral cylindrical surface portion of the spherical bush 14 and supported by a bearing, and a spherical surface portion 27c has an outer peripheral cylindrical surface portion and an inner peripheral spherical surface portion and is inserted and fixed in the hole portion 3b of the first plate member. The support member 28 supports the pair of spherical surfaces. The spherical support member 28 is fixed so that its movement in the axial direction is restricted by a nut 29 whose outer periphery is formed by a male screw. On the spherical surface portion 27a of the lever member, a boss portion 2d which is erected from the central portion of the end plate portion 2a on the side opposite to the scroll wrap portion 2b of the orbiting scroll member has an outer peripheral cylindrical surface portion and an inner peripheral spherical surface portion, and has a boss portion 2d. It is supported by a spherical pair through a spherical support member 30 inserted in the inner peripheral cylindrical surface. In the lever member 27, the distance between the center of the spherical surface portion 27c and the cylindrical surface portion 27b is the same as the distance between the center of the spherical surface portion 27c and the spherical surface portion 2.
It is formed to be sufficiently larger than the distance from the center of 7a. The spherical support members 28 and 30 have a structure that can be divided in the radial direction, and are designed so that a lever member can be easily incorporated.

With the above configuration, when the rotor portion 17 of the compressor driving motor rotates, the cylindrical surface portion 27b
Is supported at a position deviated from the rotation axis of the rotor unit 17,
The center axis of the lever member 27, whose spherical pair is supported by the spherical pair around the point on the rotation axis, has the apex at the center of the spherical pair while maintaining a constant inclination angle with respect to the rotation axis of the rotor section 17. Draw two conical loci. Therefore, the center of the spherical portion 27a of the lever member makes a circular motion, and the spherical portion 27a
An orbital motion is given to the orbiting scroll member 2 which is spherically supported by a. Since the axial position of the rotor portion 17 can be adjusted, the axial position of the spherical bush 14 mounted on the rotor portion 17 and supporting the cylindrical surface portion 27b of the lever member can also be adjusted. Yes,
The inclination angle of the central axis of the lever member 27 with respect to the rotation axis of the rotor portion 17 can be adjusted, and the revolution radius of the orbiting scroll member 2 can be adjusted. That is, the structure is such that the gap amount in the radial direction between the scroll wrap portion 2b of the orbiting scroll member and the scroll wrap portion 1b of the fixed scroll member can be adjusted. In addition, the gap amount between the tip end surface of the scroll wrap portion 2b of the orbiting scroll member and the end plate portion 1a of the fixed scroll member, and the tip end surface of the scroll wrap portion 1b of the fixed scroll member and the end plate portion 2a of the orbiting scroll member. The amount of the gap between the orbiting scroll members 2a and 2b is fixed by the structure in which the orbiting scroll member 2 is constantly pressed against the fixed scroll member 1 by applying the pressure of high-pressure gas to the surface of the end plate portion 2a of the orbiting scroll member opposite to the scroll wrap portion 2b. The amount of clearance determined by the dimensions of these members is maintained. Therefore, the end plate portion 1a of the fixed scroll member 1, the scroll wrap portion 1b, the end plate portion 2a of the orbiting scroll member 2, and the scroll wrap portion 2b form a compression chamber 31 which is a closed space. As the orbiting scroll member 2 revolves due to the rotation of the rotor portion 17 of the compressor driving motor, the compression chamber 31 moves from the outer peripheral portion to the central portion as in the scroll type compressor having the conventional structure. Reduce volume.

A first side chamber 32 and a second side chamber 33 are welded to the openings at both ends of the chamber 6 to form a closed container as a whole. The working gas flows into the compressor through the suction port 34, and the fixed scroll member 1
After passing through the inside of the suction pipe 35 that forms the suction passage toward the center, the suction chamber 35 is sucked into the compression chamber 31 from the outer peripheral portion and compressed while moving to the central portion due to the decrease in the volume, and the center of the end plate portion 1a of the fixed scroll member. Discharge port 1 formed in the section
It is discharged from c through the discharge valve 36 and the discharge valve retainer 37 into the space on the first side chamber 32 side. After that, after passing through the gap between the fixed scroll member 1 or the first plate member 3 and the chamber 6 and flowing into the motor chamber, it flows out of the compressor from the discharge port 38 provided in the chamber 6.

Due to the pressure of the compressed gas acting on the scroll wrap portion 2b of the orbiting scroll member, the load acting on the spherical surface portion 27a of the lever member 27 in the radial direction is the lever member 2
The spherical surface portion 27c and the cylindrical surface portion 27b are supported by being constrained by other parts, and the center of the spherical surface portion 27a is the load point, the center of the spherical surface portion 27c is the fulcrum, and the cylindrical surface portion 2 is
If the center of the spherical bush 14 that supports 7b is the force point, the distance between the fulcrum and the force point is sufficiently larger than the distance between the fulcrum and the load point. Significantly reduced compared to the magnitude of the load acting on the load point. Further, it is considered that the lever member 27 rotationally slides with the spherical bush 17 having a small acting load, and is unlikely to rotationally slide with the spherical support members 28, 30 having a large acting load and a large frictional resistance. .

Therefore, the lever member 27 performs only an oscillating motion having a very low sliding speed in the sliding portion on which a relatively large load acts, and the load acting on the rotary sliding portion sliding at a relatively large speed. Is significantly smaller due to the lever principle. In addition, the rotary sliding part that slides at a relatively large speed,
The two shaft portions 9a and 12a of the rotor portion 17 and the hole portions 3 of the first plate member 3 that respectively support the bearings thereof.
b and the spherical bush 20 incorporated in the central portion of the second plate member 8, there are sliding portions, but these sliding portions are on both sides of the rotation support portion by the spherical bush 14 of the cylindrical surface portion 27b of the lever member. And the cylindrical surface portion 26b of the lever member.
Since the in-plane component of the small load acting between the shaft bush 16 and the spherical bush 16 at right angles to the motor rotation axis is shared and supported, the load at the rotary sliding portions is the cylindrical surface portion 27b of the lever member 27. The load is smaller than the small load acting between the spherical bush 14 and the spherical bush 14.

The orbiting scroll member 2 is composed of a balance weight 39 fixed to the main rotor member 9 and a balance weight 40 fixed to the sub rotor member 12 in a direction forming an angle of 180 ° with the balance weight 39.
The unbalanced centrifugal force and unbalanced moment generated by the rotational movement of the lever member 27 can be completely canceled.
Further, by using a non-lubricated sliding material for each sliding surface, reliability can be improved and the lubrication operation of the compressor can be performed by relaxing sliding conditions. In addition, it is possible to operate with a non-chlorine refrigerant that has poor compatibility with the lubricating oil.

As described above, according to the embodiment of the present invention, firstly, at each sliding portion of the drive mechanism of the compressor, either one of the sliding speed and the sliding load can be significantly reduced as compared with the conventional one. ,
Mechanical friction loss is reduced and efficiency and reliability are improved. Further, according to the present embodiment, both the radial direction support and the thrust direction support of the shaft portion 12a of the auxiliary rotor member 12 are performed by the spherical bush 20 supported by the spherical pair, and the inner peripheral cylindrical surface which is the support surface thereof. Since it is easy to guarantee the accuracy of the perpendicularity between the flat portion and the flat portion of the end portion, one-sided contact does not occur at both support portions, which also improves the reliability. Further, since it is not necessary to newly form the thrust bearing with another component, the number of components can be reduced.

By adjusting the intermediate support member 18 in the axial direction, it is possible to change the inclination angle of the lever member 27 and change the revolution radius of the orbiting scroll member 2.
Since the amount of the radial gap between the scroll wrap portion 2b of the orbiting scroll member 2 and the scroll wrap portion 1b of the fixed scroll member 1 can be adjusted, the sealing property of the working gas can be improved and the performance of the compressor can be improved.

Further, the spherical support members 13 and 28 and the spherical bush support member 19 are securely fixed to the nuts 15, 22 and 29 and the intermediate support member 18 by the lock nut 21, so that unnecessary play in each part of the compressor is avoided. Can be eliminated, the entire compressor can be operated smoothly, and vibration and noise can be reduced.

[0026]

According to the present invention, in the scroll compressor, it is possible to reduce mechanical friction loss and ease sliding conditions, and to provide a scroll compressor having high performance.

[Brief description of drawings]

FIG. 1 is a side sectional view of a scroll type compressor according to a first embodiment of the present invention.

2 is a sectional view of a bearing portion of a rotor of a compressor driving motor, which is a rotating member in FIG.

[Explanation of symbols]

1 ... Fixed scroll member, 2 ... Orbiting scroll member, 2
a ... End plate part, 2b ... Scroll wrap part, 3 ... First plate member, 5 ... Oldham ring, 6 ... Chamber, 10 ...
Permanent magnets, 11 ... Cavity, 12 ... Secondary rotor member, 13 ... Spherical support member, 14 ... Spherical bush, 17 ... Motor rotor part, 18 ... Intermediate support member, 19 ... Spherical bush support member, 20 ... Spherical bush.

Claims (1)

[Claims] 1. A fixed scroll member having an end plate portion and a scroll wrap portion erected on the end plate portion, an orbiting scroll member having an end plate portion and a scroll wrap portion erected on the end plate portion, and a lever member by the fixing member. The fixed scroll member is supported by a pair of spherical surfaces centering on a point, and the orbiting scroll member is supported by the lever member by a pair of spherical surfaces centering on a point different from the spherical pair center of the fixing member, The lever member connects the two spherical pair centers to each other at a position deviated from the rotation axis by a rotating member whose axis of rotation is an axis passing through the spherical pair center of the lever member and the fixed member perpendicular to the end plate portion. The lever shaft is rotatably supported by using the elliptic axis as a relative rotation axis, and the lever is supported by the rotary member from the spherical pair support center of the fixed member of the lever member. Drive mechanism for imparting an orbital motion to the orbiting scroll member by making the distance to the orbiting part larger than the distance from the center of spherical pair support of the fixed member of the lever member to the center of spherical pair support of the lever member of the orbiting scroll member. And a rotation preventing mechanism for preventing rotation of the orbiting scroll member, and a closed space formed by the end plate portion of the fixed scroll member, the scroll wrap portion, and the end plate portion of the orbiting scroll member and the scroll wrap portion. In a scroll type compressor that compresses gas by utilizing that the volume of the rotary scroll member changes with the orbital movement of the orbiting scroll member, the shaft portion of the rotary member, which is a component of the drive mechanism, has a cylindrical inner circumference. Is rotatably supported by a spherical bush having a surface, a spherical outer peripheral surface, and a flat end surface, and the flat surface of the spherical bush. Scroll compressor characterized in that it is restricted to move in the thrust direction by the end face of the.