JPH0778390B2 - Rotary fluid machinery - Google Patents

Description

TECHNICAL FIELD The present invention relates to a rotary gas compressor used for a cooler or the like.

2. Description of the Related Art One of the compressors is a scroll type compressor. This is because a pair of vortex rolls are engaged with each other at an angle, and give a relative circular motion (revolution motion only) to move the closed small chamber formed between the vortex rolls toward the center. However, this is a positive displacement compression device in which the volume of the small chamber is gradually reduced to compress the fluid in the small chamber and the compressed fluid is discharged from the central portion.

The principle of such a scroll type fluid machine has been known for a long time. 4 (1), (2), (3), and (4) show the operating principle of the scroll compressor. If two vortex windings 1 and 2 having the same shape are arranged so that they are relatively 180 ° out of phase with each other and are engaged with each other, as shown in FIG. The small chambers 3a and 3b are formed between the points a ₁ and b ₁ and the points a ₂ and b _{2 which} are in contact with each other. Here, one spiral member 2 is fixed, and the other spiral member 1 is spirally wound around the center 0 of the spiral member 2 with the center 0'of the spiral member 1 having a radius 00 '. When the body 1 revolves while inhibiting its rotation, the volumes of the sealed small chambers 3a and 3b gradually change.

When the vortex winding body 1 is revolved 90 ° from the state shown in FIG. 4 (1), the state shown in FIG. 4 (2) is obtained, and when it is revolved 180 °, the state shown in FIG. 4 (3) is obtained, 270 ° When revolved, it will be in the state shown in Fig. 4 (4), during which the small chambers 3a, 3b
The volume gradually decreases, and in the states shown in FIGS. 4 (4) to (1), the two small chambers 3a and 3b communicate with each other to form the small chamber 3. This small chamber 3 is further rotated by the revolution of the vortex winding body 1 as shown in FIG.
The state shown in FIG. 4 (3) and the volume thereof are reduced to the minimum volume between FIGS. 4 (3) and 4 (4). Here, a compressed end fluid is provided by providing a seal end plate on the axial end faces of the two spiral wound bodies 1 and 2 and providing a discharge port 4 at substantially the center of the seal end plate of one spiral wound body. Is exhaled from here. During this time, the outer space that started to open in FIG. 4 (2) moves from FIG. 4 (3) and FIG. 4 (4) to FIG. 3b
Is formed, and this is repeated thereafter.

The actual scroll compressor based on the above-mentioned operating principle is
A spiral end plate having a discharge port at approximately the center is integrally fixed to one end face, and one vortex roll is fixed, and the other end of the same shape also has a seal end plate integrally on one end face. The winding body is 180 ° out of phase with the one spiral winding body,
In addition, the two spirals are overlapped with each other while being relatively displaced by a distance 2ρ (= the pitch of the spiral of the spiral and the plate thickness of the spiral) so that the other spiral can be prevented from rotating and revolve. Further, the other spiral winding body is rotated around the center of one spiral winding body (corresponding to 0 in FIG. 4) with a crank mechanism having a crank radius ρ (the fourth spiral movement (fourth rotation)).
(In the figure, the orbital motion of 0'with radius ρ centered on 0)
Is configured.

FIG. 3 shows a schematic structure of a conventional scroll type compressor configured as described above.

The fixed scroll 20 (corresponding to one spiral member 2 in FIG. 4) includes a spiral portion 21, a seal end plate 22, and a discharge hole 23 provided in the seal end plate 22, and the fixed scroll 20 is attached to a casing 30. Fixed.

The orbiting scroll 10 (corresponding to the other spiraling body 1 in FIG. 4) comprises a spiraling portion 11, a seal end plate 12, and a drive portion 14 having a bearing 13 for driving the orbiting scroll 10.

Further, 15 is a bearing that receives the thrust load of the orbiting scroll 10, and the orbiting scroll 10 is casing through the bearing 15.
Support within 30.

Further, 16 is a rotation prevention revolution mechanism (for example, Oldham's joint) for inhibiting rotation of the revolution scroll 10 and causing revolution movement, and the revolution scroll 10 is connected to the casing 30 via this rotation prevention revolution mechanism.

The drive shaft 40 having the crankpin radius ρ is
Is installed via bearings 41 and 42. Reference numeral 31 is an inlet provided in the casing 30, and 32 is an outlet provided in the casing 30.

In such a device, when the drive shaft 40 is rotated, the orbiting scroll 10 causes an orbital (orbiting) motion with a radius ρ due to the action of the rotation prevention and revolution mechanism 16, and passes through the suction port 31 from the outside of the casing 30 ( (Fig. 3 mark) The fluid is compressed by the two scrolls 10 and 20 that have been sucked in, and the compressed fluid passes through the fixed scroll 20 through the discharge hole 23 and is sent to the outside from the discharge port 32 provided in the casing 30. Be issued.

The detailed operation of this device is as described with reference to FIGS. 4 (1) to 4 (4).

Also, one in which two scrolls are rotatable is disclosed in Japanese Patent Laid-Open No.
-110885. This is one in which a discharge port is bored inside one of the rotating shafts of two rotatable scrolls, and compressed gas is taken out from the discharge port through a discharge chamber.

Problems to be Solved by the Invention In the former orbiting scroll that does not rotate but only revolves, it is necessary to incorporate a rotation preventing revolution mechanism having large torque transmission capability and durability, and the entire compressor is large. In addition, the price increases, and in the latter two scrolls which are rotatable, the position and size of the discharge port are restricted when the discharge port is provided.

MEANS FOR SOLVING THE PROBLEMS The present invention allows a pair of vortex winding bodies to be overlapped with each other so that the closed small chambers are limited by the vortex winding bodies by shifting the phases of the vortex winding bodies, and the both vortex winding bodies are rotatable about their respective central axes. In a rotary fluid machine that supports and rotates one vortex winding body to rotate the other vortex winding body in the same direction and in the same phase, the both vortex winding bodies are installed in a casing,
A discharge chamber is formed between the casing and the rear surface of the end plate of the driven side spiral body, and a bearing portion protruding into the discharge chamber is provided in the casing to rotatably support the rotary shaft of the driven side spiral body. A discharge hole for communicating the closed small chamber and the discharge chamber is provided at a position eccentric to the rotary shaft of the end plate of the driven side spiral member.

Operation The operation principle of the present invention is shown in FIG. 2 in comparison with the principle diagram (FIG. 4) of the conventional scroll type gas machine.

The rotation angle of 90 ° pitch is shown in FIG. 4, while the rotation angle of 45 ° pitch is shown in FIG. 2 for easy understanding.

When a pair of spirals 501 and 502 are arranged so that they are relatively 180 degrees out of phase with each other and are engaged with each other, as shown in FIG.
_1, b ₁ and point a _2, b sealed chamber 503a between _2, 503b are formed (so far same as that of the conventional scroll type fluid machine) where one spiral body 501 an arbitrary point G Rotate around.

Here, point p is the center of one spiral body 501, point p ′ is the center of the other spiral body 502, point G is the center of rotation of one spiral body 501, and point G ′ is the center of rotation of the other spiral body 502. And Determine the relationship between them so that

In addition, here, a case where an involute curve is used as a basic shape of both spiral bodies 501 and 502 is shown,
The points p and p'represent the center of the base circle of each involute curve.

When the one spiral member 501 is rotated about the point G and the other spiral member 502 is rotated in the same direction about the point G ′, the volumes of the sealed small chambers 503a and 503b are gradually changed.

From the state shown in FIG. 2 (1), when the vortex wound bodies 501, 502 are rotated by 45 ° around the respective rotation centers G, G ', the state shown in FIG. As shown in Fig. (3), when rotated 135 °, it becomes the condition of Fig. 2 (4), when rotated 180 °, it becomes the condition of Fig. 2 (5), and when rotated 225 °, it becomes the condition of Fig. 2 (6). The state becomes as shown in Fig. 2 (7) when rotated 270 °, and becomes the state as shown in Fig. 2 (8) when rotated 315 °.

During this period, the volumes of the small chambers 503a, 503b gradually decrease, and in the states shown in FIGS.
03b starts communicating and becomes small room 503. That is, in FIG. 2 (8) and thereafter, the small chambers 503a and 503b communicate with each other to form one small chamber 503, and the rotation progresses from the state of FIG. 2 (1).
(3)->(4)->(5)->(6)->(7)-> (8).

Note that the ▲ ▼ in FIG. 2 rotates while maintaining the same relationship as the ▲ ▼ in FIG. 4 is always constant,
The contact relationship between the two spirals is the same as in FIG.

Here, a seal end plate is provided on the axial end faces of the two spiral wound bodies 501 and 502, and a discharge port is provided near the center of one or both of the spiral wound bodies of one of the two spiral wound bodies 501 and 502. (Not shown).

The compressed fluid in the small chamber 503 is discharged from here.

During this time, the outer space that started to open in Fig. 2 (2)
Fig. 2 (3) → (4) → (5) → (6) → (7) →
Moving to (8), in FIG. 2 (1), new fluid is taken in to form the closed small chambers 503a and 503b, and this is repeated thereafter.

Practical Example In FIG. 1, a driven scroll 600 (corresponding to the other spiral wound body 502 in FIG. 2) has a spiral wound portion 601, a seal end plate 602, and a discharge hole 603 provided on the seal end plate 602. Become bearing 604
It is rotatably supported in the casing 700 via.

Further, 605 is a bearing that receives the thrust load of the driven scroll 600, and 606 is a seal mechanism between the driven scroll 600 and the casing 700.

The rotary scroll 800 (corresponding to one spiral body 501 in FIG. 2) is composed of a spiral portion 801 and a seal end plate 802, and the rotary scroll 800 is integrally formed with a drive shaft 803, bearings 804, 805 and rotations. It is rotatably supported in the casing 700 via a bearing 806 that receives the thrust load of the scroll.

In addition, in order to rotate the driven scroll 600 and the rotary scroll 800 in the same direction and in the same phase, an appropriate manufacturing means is incorporated between both scrolls.

Reference numeral 701 is an inlet provided in the casing 700, and 702 is an outlet provided in the casing 700.

In addition, the casing 700 and the seal end plate 60 of the driven scroll 600
A discharge chamber 810 is formed between the rear surface and the back surface of 2.

By configuring and arranging each member as described above, the operation described in FIG. 4 is caused, and a new compressor completely different from the conventional one is configured.

That is, the drive shaft 8 integrally formed with the rotary scroll 800.
When 03 is rotated, the rotary scroll 800 produces a rotary motion, and the suction compression and discharge actions occur between the two scrolls 800 and 600 as shown in the principle diagram.

Scroll from outside casing 700 through inlet 701
The fluid absorbed between 800 and 600 has two scrolls 8
It is compressed by 00,600 and is sent out from the discharge port 702 of the casing 700 through the discharge hole 603 provided in the driven scroll 600.

EFFECTS OF THE INVENTION As described above, according to the present invention, a pair of vortex winding bodies are installed in a casing, and a discharge chamber is formed between the casing and the end plate rear surface of the driven side vortex winding body, and the discharge chamber is provided in the casing. A bearing portion projecting inward is provided to rotatably support the rotary shaft of the driven side spiral member, and the closed small chamber and the discharge chamber communicate with each other at a position eccentric to the rotary shaft of the end plate of the driven side spiral member. Since the discharge hole is provided, the degree of freedom in design is increased in the installation position and size of the discharge hole, and there is no protrusion in the discharge chamber to prevent pulsation of the discharge chamber. Since it is not necessary, the structure of the device is simplified, and the size of the entire device can be reduced.

[Brief description of drawings]

FIG. 1 is a schematic sectional view of an embodiment of the rotary fluid machine of the present invention,
FIG. 2 is an operation principle diagram of the present invention, FIG. 3 is a schematic sectional view of a conventional device, and FIG. 4 is an operation principle diagram of the conventional device. 600 ... driven scroll, 603 ... discharge hole, 604 ... bearing, 800 ... rotary scroll, 803 ... drive shaft, 804,805,806 ... bearing, 700 ... casing, 701 ... suction port, 702 ... discharge port

Claims (1)

[Claims] 1. A pair of vortex winding bodies are overlapped with each other so that the closed small chambers are limited by both vortex winding bodies, and the two vortex winding bodies are rotatably supported about their respective central axes, and one vortex winding body is supported. In a rotary fluid machine that rotationally drives the body to rotate the other spiral body in the same direction and in the same phase, the both spiral bodies are installed in a casing, and the casing and the end plate rear surface of the driven spiral body are A discharge chamber is formed between them, and a bearing portion protruding into the discharge chamber is provided in the casing to rotatably support the rotary shaft of the driven side spiral member, and the rotary shaft of the end plate of the driven side spiral member is A rotary fluid machine characterized in that a discharge hole is provided at an eccentric position so as to connect the closed small chamber and the discharge chamber.