JPS62191685A - Scroll compressor - Google Patents

Abstract

PURPOSE:To eliminate necessity for use of Oldham's joint by arranging a follower shaft with its axis in a specific distance to the axis of a driving scroll, and rotating a follower scroll in synchronization with rotation of said driving scroll through contacting of spiral projections of the two scrolls. CONSTITUTION:A driving scroll 1 is provided at its disc part 1b with a spiral projection 1a, and there a drive shaft 4 is installed solidly as in a single piece. A follower scroll 2 is alike equipped at its disc part 2b with a spiral projection 2a, which is combined with the first named spiral projection 1a, and there a follower shaft 5 and a discharge port 2c are provided. The distance L between the centers O1, O2 of these scrolls 1, 2 can, for ex., be expressed as L=p/2-t, where p and t represent pitch of scroll and thickness of spiral projection, respectively. Thereby the follower scroll 2 is put in synchronous rotation with the driving scroll 1 through contacting of the side faces of said spiral projections 1a, 2a, and a compression chamber 3 formed between spiral projections 1a, 2a is moved to the center from the outside so as to provide compressive action.

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a fully rotating scroll compressor that rotates a driving scroll and a driven scroll.

[Conventional technology]

The principle of a scroll compressor has been known for a long time, and it is a type of positive displacement compressor that performs compression by combining a pair of spiral protrusions. 7~Usually, one of the spiral protrusions is fixed and the other is oscillated to perform the compression action, but both spiral protrusions are rotated around their respective centers, which is the so-called whole system rotation type. The principle is well known.

A diagram of the principle of this fully rotary scroll compressor is shown in FIG. The drive scroll 1 has a single electric motor engine.

Or, it rotates around its axial center O1 by a drive source such as a turbine. The driven scroll 2 is also rotated about its center 02 in synchronization with the rotation of the driving scroll 1. Due to both rotations, the υ compression chamber 3 moves toward the center and reduces its volume, the pressure of the compressed gas rises, and the compressed gas is discharged as high-pressure gas from the discharge port 2c.

In state 2 of FIG. 2(a), gas is sucked into the compression chamber 3, and from 0° to 90° as shown in FIG. 2(b) to (d).
By rotating ゜→]8o0→270°→360° (0°), the compression chamber 3 gradually moves toward the center and its volume decreases.

During this time, the spiral projections 1a of both scrolls 1.2,
It can be seen that the radial seal portion S according to 2a is aligned in a straight line in the radial direction and occupies a constant position tcit in a stationary state.

A conventional fully rotary type scroll compressor is shown in US Pat. As a means, an Oldham joint is used.

[Problem that the invention seeks to solve]

The conventional scroll compressor described above has a sliding part, and this sliding surface undergoes reciprocating motion.
The weight is considerably large, and the structure is not suitable for high-speed rotation! There was an IA point.

In addition, the Oldham joint is disposed surrounding the outer periphery of both scrolls, and there is a problem in that the outer diameter becomes large.

The present invention has been made to solve these problems, and aims to provide a scroll compressor with a small number of parts, a simple structure, high speed, high efficiency, and low vibration.

[Means for solving problems]

This scroll compressor according to the present invention K has a driven scroll provided with a driven shaft and a driven scroll provided with a driven shaft spaced apart from each other by a predetermined axis center interval, and both spiral protrusions are arranged in a radial direction. It is designed to make contact at the seal part.

[For Kui]

In this invention, when the driving scroll rotates, the driven scroll, which is spaced apart from it by a predetermined axial center distance, rotates synchronously due to the contact between the seal portions of both spiral protrusions, compressing the gas. It is squeezed out. In this way, the driven scroll is rotated synchronously with respect to the driving scroll without the need for an Oldham coupling.

〔Example〕

FIG. 1 is a longitudinal sectional view of an embodiment of a scroll compressor according to the present invention. In the figure, 1 is a driving scroll;
A spiral protrusion 1a is provided on the disk portion 1b, and a drive shaft 4 is integrally formed or fixed thereto.

21I'i A driven scroll corresponding to the driving scroll 1, a spiral protrusion 2a provided on a disk portion 2b is combined with a spiral protrusion 1a (see Fig. 2), and a driven shaft 5 is integrally formed or It is fixed, and a discharge port 2C is provided.

The distance between the axial center 01 of the driving scroll 1 and the axial center 02 of the driven scroll is L==p/2-t, where p is the pitch of the scroll and t is the thickness of the spiral protrusion.

6 is a sealed container, 7 is a lower bearing support fixed to this container, the drive scroll l is supported from below by a thrust bearing 8, and the drive shaft 4 is supported in the radial direction by bearings 9 and 1°. . Reference numeral 11 denotes an upper bearing support attached to a support 12 fixed to the container 6 by means of a port 13. The driven scroll 2 is received from above by a thrust bearing 14, and the driven shaft 5 is supported in the radial direction by bearings 15 and 16. There is.

Reference numeral 17 denotes an electric motor as a drive source, which is supported by a support member 32 fixed to the container 6 and consists of a stator core 19 to which a stator coil 19 is attached, and a rotor 20 fixed to the drive shaft 4.

Next, 21 is an oil sump provided at the upper end of the upper bearing support 11, 22 is an end plate attached to the upper part of this oil sump 21 with a bolt 23, and 24 is a rotating mechanical part attached to the end of the driven shaft. A seal 25 is a fixed mechanical seal attached to the end plate 22 and in contact with the mechanical seal 24 to prevent leakage of compressed gas; 26 is a chip seal fitted in a sealing groove IC provided at the upper end of the spiral protrusion 1a;
27 is a sealing groove 2 provided at the lower end of the spiral protrusion 2a.
This is the chip seal fitted in d. 28 is the drive shaft 4
29 is an oil supply pipe that guides lubricating oil from this oil pump into the upper oil sump 21; 30 is a suction pipe that is attached to the container 6 and leads gas to the scroll part;
31 is a discharge pipe fixed to the end plate 22 and guides compressed gas from the discharge port 2C to the outside; 33 is lubricating oil stored at the bottom of the container 6;

The operation of the compressor in the above embodiment is as follows. When the electric motor 17 is rotated, the drive scroll 1 rotates around the center 01.If we pay attention to the left part A of the radial seal parts S of both scrolls 1 and 2 shown in FIG. In part A, the outer peripheral side of the spiral projection 2a of the driven scroll 2 corresponds to the inner peripheral side of the spiral projection 1a of the driving scroll 1. At this point A, the spiral protrusion 1a
Since the inner circumferential side moves so that the radius decreases when viewed from the center 01, it inevitably comes into contact with the outer circumferential side of the spiral protrusion 2a,
The driven scroll 2 is driven to rotate.

In this state, the driven scroll 2 is driven to rotate, but if the driven scroll 2 is
If an attempt is made to rotate faster, a gap will be created in section A of P, Figure 2 (1)), and the driving force will not be transmitted. However, in such a state, the spiral protrusion 2
The inner radius of a decreases, and the spiral protrusion 1a
Since the radius on the outer circumferential side of the scroll is increased, the two come into contact with each other, and the driven scroll 2 is automatically restricted from rotating faster than the driving scroll 1.

Considering this, it is possible that the driving scroll 1 and the driven scroll 2 will come into contact with each other at the A part or B part of the spiral protrusions 1a and 2a, and both will rotate synchronously even if the conventional Oldham coupling means is eliminated. Become. This is the gist of the technical idea of the present invention.0 When both the driving scroll 1 and the driven scroll 2 are performing compression operation, half of the torque associated with compression is applied to the driving scroll 1 and the electric motor 17. However, since only compression torque is applied to the driven scroll 2, the driven scroll 2 attempts to rotate about its center 02 in the opposite direction to the driving scroll 1. At this time, they come into contact at part A in FIG. 2(b), and reverse rotation is prevented at this part to continue compression operation. .

When the driving scroll 1 enters deceleration operation due to stopping, etc., the driven scroll 2 tries to rotate quickly due to its inertia, but in this case as well, as explained above, both scrolls come into contact at part B in Fig. 2(b) and both scrolls 1.2 rotates synchronously.

If there is no gap between the driving scroll 1 and the driven scroll 2 at the seal portion S in the radial direction, the phase relationship between both scrolls will be maintained reliably. There is a gap ε, and the phase relationship between both scrolls may be shifted by the gap. In this case, the shape of the spiral protrusions 1a and 2a is an involute curve, and its base circle
clθ), the angular deviation Δθ between both scrolls is given by Δθ=6/a from the geometric relationship aΔθ=ε.

The relative motion between the driving scroll 1 and the driven scroll 2 causes suction, compression, and discharge actions as shown in FIG. 2. The compressed gas is forced out from the discharge port 2C. At this time, the driven unit 1ia5 is rotating, but due to the dynamic seal between the rotating mechanical seal 24 and the fixed mechanical seal 25, the discharged compressed gas is forced out without leaking.

Due to the driving rotation of the drive scroll 1, gas is sucked into the container 6 from the suction pipe 29, and the electric motor 17 and the upper bearing support 7. A gas passage for cooling each bearing through the lower bearing support 11 (not shown) is drawn to the outer periphery of the scroll portion and into the compression chamber 3 formed by both scrolls 1.2.

The rotation of the drive shaft 4 causes the oil pump 28 to rotate, and the lubricating oil 3J is sent to the oil sump 21 through the oil supply pipe 29, lubricating the mechanical seals 24 and 25, and sealing the bearings xa and 1.
6.

Lubricate the thrust bearings 14, B, and bearings 9, 10,
It is returned to the inner bottom of the container 6.

In addition, in this invention, the Orgum a method is omitted,
Since the spiral projection 2a of the driven scroll 2 is driven in direct contact with the spiral projection 1a of the driving scroll 1, both materials are made of different materials to create a combination with less wear, and the contact portion (
The wear of parts (A and B in Figure 2) should be reduced.

Further, the contact surfaces of both spiral protrusions 1a and 2a may be coated with a wear-resistant material.

In general, in order to reduce the contact noise between both scrolls 1 and 2, a self-lubricating material may be fixed to at least one of the contact surfaces of both spiral protrusions 1a and 2a. Alternatively, at least one of the spiral projections itself may be made of a wear-resistant self-lubricating material.

〔Effect of the invention〕

As described above, according to the invention, the center of the driven shaft of the driven scroll is arranged at a predetermined distance from the center of the drive shaft of the drive scroll, and the rotation of the drive scroll seals both spiral protrusions. Since the driven scrolls are rotated synchronously by contact at the parts, there is no need for Oldham's coupling means, the number of parts is reduced, the size is reduced, the groove bottom is simple and inexpensive, and high speed, 0 has the effect of providing high efficiency and low vibration.

[Brief explanation of drawings]

FIG. 1 is a longitudinal cross-sectional view of an embodiment of a scroll compressor according to the present invention, and FIG. 2 is a diagram showing the operating principle of a fully rotating scroll compressor. 1... Drive scroll, 1a... Spiral protrusion, 11
)... Disk portion, 2... Driven scroll, 2a...
Spiral projection body, 2b...disc part, 3...compression chamber, 4.
. . . Drive shaft, 5 . . . Drive shaft. In the drawings, the same reference numerals indicate the same or corresponding parts.

Claims (3)

[Claims] (1) A drive scroll that is rotatably supported by a fixed part and is rotatably driven, is provided with a disc part, and a spiral protrusion is provided on this disc part, and the shaft center corresponds to this drive scroll. The driven shafts are arranged at predetermined intervals and rotatably supported by a fixed part, and a disc part is provided on the driven shaft, and a spiral protrusion is provided on this disc part, and this spiral protrusion is used for the above-mentioned drive. A driven scroll is combined with the spiral protrusion of the scroll, and both of the spiral protrusions are brought into contact with their sides, so that the driven scroll follows the rotation of the driving scroll and rotates synchronously, forming a structure between both of the spiral protrusions. A scroll compressor characterized in that the compression chamber moves from the outside to the center to perform compression. (2) The scroll compressor according to claim 1, wherein both spiral protrusions are made of a combination of different materials to reduce contact wear. (3) The scroll compressor according to claim 1, wherein at least one of the contact surfaces of both spiral protrusions is coated with a wear-resistant material. (4) The scroll compressor according to claim 1, wherein a self-lubricating material is fixed to at least one of the contact surfaces of both spiral protrusions.