JPH07310684A - Scroll type compressor - Google Patents

Abstract

PURPOSE:To secure a sufficient suction quantity of a fluid and at the same time make the whole of a compressor small and lightweight. CONSTITUTION:A first blade 24 of a scroll-form and a second blade 34 of a scroll-form are rotated about the respective central axes O1, O2 at an equal angular speed whereby a fluid is sucked, compressed and then discharged into an operation chamber between both blades 24, 34. The outer part in the radial direction of the first blade 24 is eliminated, and the terminal part of the outside of the remaining part is made into a circular arc-like sliding surface 10a sliding on the inner circumferential surface 10a of a cylindrical housing, thereby using the inner circumferential surface 10a also as the inner circumferential surface of the eliminated part of the first blade.

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 used for an engine supercharger or the like.

[0002]

2. Description of the Related Art Conventionally, a scroll compressor disclosed in Japanese Patent Laid-Open No. 2-67487 has been known. This compressor includes a first scroll member having a circular side wall formed with scroll-shaped ribs (blades), and a second scroll member having a rib arranged inside the rib of the first scroll member. , The working chamber is formed between the two blades by contact between the two blades, and both scroll members simultaneously rotate in an eccentric state at the same angular velocity, so that the fluid is sucked into the working chamber and discharged from the central portion. It is like this.

22 to 26 show an example of such a compressor.
Shown in. The first scroll member 80 is rotatably held in the housing 100 about the central axis O ₁ , and the central axis O _{2 is} eccentric from the central axis O ₁ by a predetermined amount e.
The second scroll member 90 is rotatably held around. The first scroll member 80 has a scroll-shaped first blade 84 protruding from the first side wall 82, and the second scroll member 90 has a circumscribed circle more than the first blade 84 on the second side wall 92. Small scroll-shaped second blade 9
4 is projected. And both blades 84, 94
Both ends in the axial direction of the working chamber formed between them are covered with the both side walls 82, 92.

Here, the first blade 84 and the second blade 9 are
The outer end portions of 4 are arcuate large diameter portions 84a and 94a centered on the central axes O ₁ and O ₂ , respectively.

In such a compressor, both scroll members 80 and 90 are simultaneously driven to rotate at eccentric states at equal angular velocities, thereby performing suction, compression, and discharge of fluid.

Concretely, first, as shown in FIG.
Inner surface of large-diameter portion 84a of blade 84 and large-diameter portion 9 of second blade 94
An outer working chamber 89A is formed between both blades 84 and 94 when the outer surface of the outer working chamber 89A contacts the outer working chamber 89A.
The fluid sucked from the suction port 102 is sealed inside. When the scroll members 80, 90 rotate 90 ° clockwise in FIG. 24 from this state to the state of FIG. 22, the outer working chamber 89A is reduced in volume and the fluid in the outer working chamber 89A is compressed. To be done. When it further rotates 90 ° to the state shown in FIG. 25, the inside of the outer working chamber 89A becomes close to the maximum pressure, while the first inner surface of the second blade 94 has the first pressure.
The outer surfaces of the blades 84 start to come into contact with each other to form an inner working chamber 89B between the blades 84 and 94. After further rotating by 90 ° and passing through the state shown in FIG. 26, the outer working chamber 89A is opened to the discharge port 95, and the fluid in the outer working chamber 89A is discharged from the discharge port 95 under high pressure. By further rotating 90 ° from this state, the state shown in FIG. 24 is restored, and thereafter, the same suction and discharge as described above are repeated.

[0007]

In the scroll compressor, as shown in FIG. 24, the large diameter portion 94 of the second blade 94 is provided.
a The larger the volume of the outer working chamber 89A formed by the outer peripheral surface coming into contact with the inner peripheral surface of the large diameter portion 84a of the first blade 84, the greater the amount of fluid suction that can be secured. It is preferable that the arc-shaped large diameter portion 84a is formed over a wide angle range. However, forming such a long large-diameter portion 84a greatly hinders downsizing and weight reduction of the entire compressor. In recent years, in particular, the use of the compressor as a supercharger for an engine has been studied, and there is an increasing demand for reduction in size and weight.

An object of the present invention is to provide a scroll type compressor which can solve such problems.

[0009]

As a means for solving the above problems, the present invention provides a first scroll member having a scroll-shaped first blade, and a second blade disposed inside the first blade. A second scroll member having a
A housing for rotatably holding the scroll member and the second scroll member at positions eccentric to each other, and the fluid is sucked into the working chamber between the blades by rotational movement of both scroll members at equal angular velocities. In a scroll type compressor configured to discharge from a central portion, an inner peripheral surface of a portion for housing both blades in the housing is a cylindrical surface, and a radially outer portion of the first blade is partially removed and left. The outer terminating end of the portion is a sliding portion slidable over the entire inner peripheral surface of the housing, and the working chamber is formed between the inner peripheral surface of the housing and the outer surface of the second blade. (Claim 1).

In this compressor, the outer end surface of the first blade is an arcuate sliding surface along the inner peripheral surface of the housing, and a labyrinth seal portion is formed on the sliding surface (claim 2). After the inner end portions of the blades are in contact with each other, the outer surface of the second blade is in contact with the inner surface of the outer end portion of the first blade, and then the inner blade end portions are separated from each other. It is more preferable to set the shape of the second blade (claim 3).

In this compressor, a side wall that covers one axial end of the first blade is provided on the first scroll member, and a suction port is opened in the side wall, and a fluid is axially passed from the suction port into the working chamber. The suction port for sucking fluid from the radial direction may be opened in a part of the inner circumferential surface of the housing in the circumferential direction, and the suction port The position of one end in the axial direction is set to the contact point between the outer surface of the second blade and the inner peripheral surface of the housing or to the position downstream of the contact point in the rotational direction of both scroll members, and the position of the other end of the suction port. May be set at a position substantially equal to the position reached by the sliding portion of the first blade when the outer surface of the second blade starts to contact the inner peripheral surface of the housing (claim 5).

Further, the radius of the inner peripheral surface of the housing and the first centering around the rotation center of the first scroll member.
The radius of the circumscribed circle of the sliding portion of the blade is the radius of the circumscribed circle of the second blade, and the eccentric amount between the rotation center axis of the first scroll member and the rotation center axis of the second scroll member. The second circular arc surface having a radius of curvature equal to the radius of the circumscribed circle of the second blade about the rotation center axis of the second scroll member is set on the inner peripheral surface of the housing and is set to be smaller than the sum. By arranging in the eccentric direction of the central axis, a more excellent effect as described later can be obtained (claim 6). In this case, the radius of the inner peripheral surface of the housing and the rotation center of the first scroll member are set so that the central angle of the second arc surface is smaller than the angular width of the sliding portion of the first blade in the circumferential direction. It is more preferable to set the circumferential width of the circumscribed circle of the sliding portion of the first blade centered at (Claim 7).

[0013]

According to the scroll compressor of claim 1,
Despite the removal of the radially outer portion of the first blade, the sliding portion, which is the outer end portion of the remaining portion, rotates while sliding on the inner peripheral surface of the cylindrical housing, A working chamber is formed by the inner peripheral surface of the housing and both blades, and the fluid sucked into the working chamber is compressed and discharged from the central portion. As described above, the inner peripheral surface of the housing is also used as the inner peripheral surface of the radially outer portion of the first blade, so that the first blade and the housing that houses the first blade are reduced in size and weight.

Here, in the compressor of the second aspect, the outer end surface of the first blade is an arcuate sliding surface along the inner peripheral surface of the housing, and the labyrinth seal portion is formed on this sliding surface. Therefore, compared with, for example, a structure in which the outer end portion of the first blade is in substantially linear contact with the inner peripheral surface of the housing, the leak resistance is increased and the sealing performance is improved at the sliding portion.

Further, in the compressor of the third aspect, after the inner end portions of both blades contact each other, the inner surface of the outer end portion of the first blade contacts the outer surface of the second blade.
That is, the inner end portions are not separated from each other until the sliding portion is separated from the central discharge port by the contact between both blades, and the inner end portions contact each other so that the sliding portion is at the center. Separated from the outlet. Therefore, the sliding portion is not directly communicated with the discharge port from beginning to end, and there is no possibility that the fluid discharge pressure (high pressure) directly acts on the sliding portion and the fluid easily leaks from the sliding portion.

In the compressor according to the fourth aspect, one end of the first blade is covered with a side wall, and a fluid is sucked into the working chamber between the blades in the axial direction through the suction port provided in the side wall without any trouble. To be done.

On the other hand, in the compressor according to claim 5,
A fluid is sucked into the working chamber from a radial direction through a suction port opened in a part of the inner circumferential surface of the housing in the circumferential direction. Here, one end of the suction port is located at a contact point between the outer surface of the second blade and the inner circumferential surface of the housing, or at a position downstream of the contact point in the rotation direction of both scroll members. Since the end position is substantially the same as the position where the sliding portion of the first blade reaches at the time when the outer surface of the second blade and the inner peripheral surface of the housing start to contact, the contact start time or this contact start After a short time, the working chamber formed between the blades will be surely isolated (that is, sealed) from the suction port, and the fluid trapped in the working chamber will be sure. Is compressed to.

According to a sixth aspect of the present invention, both the radius of the inner peripheral surface of the housing and the radius of the circumscribed circle of the sliding portion of the first blade about the rotation center of the first scroll member are set together. , The radius of the circumscribed circle of the second blade and the first
It is smaller than the sum of the eccentric amounts of the rotation center axis of the scroll member and the rotation center axis of the second scroll member, and the second blade is provided on the inner peripheral surface of the housing with the rotation center axis of the second scroll member as the center. Since the second circular arc surface having a radius of curvature equal to the radius of the circumscribed circle is recessed in the eccentric direction of the both rotation center axes, the radius of the inner peripheral surface of the housing,
The outer peripheral surface of the second blade protruding from the circumscribed circle of the first blade by setting the radius of the circumscribed circle of the sliding portion of the first blade around the rotation center of the first scroll member is equivalent to this outer peripheral surface. It comes into surface contact with the second arc surface having the radius of curvature of. Therefore, as compared with the case where the outer peripheral surface of the second blade is in direct line contact with the inner peripheral surface of the housing having a larger radius of curvature than this outer peripheral surface, the sealability at this contact portion is further improved.

When the sliding portion of the first blade passes over the second circular arc surface, a momentary gap is created between the second circular arc surface and the sliding portion. If the shape of both blades is set so that a closed working chamber is not yet formed between the two blades at this point, the airtightness of the working chamber is not impaired. Further, in the compressor according to claim 7, the radius of the inner peripheral surface of the housing and the radius of the inner peripheral surface of the housing such that the central angle of the second arc surface is smaller than the angular width of the sliding portion of the first blade in the circumferential direction. The radius of the circumscribed circle of the sliding portion of the first blade about the rotation center of the first scroll member is set, and when the sliding portion passes over the second circular arc surface, Since the sliding portion completely covers the two circular arc surfaces, even if the blade shape is set so that the working chamber is formed when passing through, the hermeticity of the working chamber is not impaired.

[0020]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A first embodiment of the present invention will be described with reference to FIGS.

The scroll compressor shown in FIGS. 1 and 2 is provided with a cylindrical central housing 10 and side wall housings 12 and 14 mounted in front of and behind the central housing 10. A suction port 16 is formed in one side wall housing 12, and a donut-shaped suction passage 17 that connects the suction port 16 and the inside of the central housing 10 is formed. A discharge port 38 is formed. And the housing 1
The first scroll member 18 and the second scroll member
The scroll member 20 is housed.

The first scroll member 18 is shown in FIG.
As shown in (b), it has a disk-shaped first side wall 22, and one surface of the first side wall 22 has a first blade 24.
And a shaft 26 is provided at the center of the other surface. The shaft 26 has a bearing 27,
A pulley 30 is rotatably supported by 28, and a pulley 30 is fixed to the tip of the shaft 26. The pulley 30 is connected to a rotary drive source via a belt (not shown), and the operation of the rotary drive source causes the entire first scroll member 18 to move to the shaft 2
It is adapted to be driven to rotate around the central axis O _{1 of} 6. Further, the suction port 21 is cut out in the first side wall 22, and the fluid in the suction passage 17 is sucked through the suction port 21. Note that FIG.
In (a), 22b is a hole for mounting a link plate 46 described later.

The second scroll member 20 is shown in FIG.
As shown in (b), it has a disc-shaped second side wall 32, one surface of the second side wall 32 is provided with a second blade 34, and the other surface has a center at the center thereof. A cylindrical portion 36 is provided so as to project. The cylindrical portion 36 is rotatably supported inside the side wall housing 14 by bearings 40 and 42 at a position where it is connected to a discharge port 38 formed in the side wall housing 14.
As a result, the entire second scroll member 20 is rotatable about the central axis O ₂ of the cylindrical portion 36.

Here, the central axes O ₁ and O ₂ are shown in FIG.
As shown in (4), it is in a state of being eccentric by a certain amount e.

The inner peripheral surface 10a of the central housing 10 for accommodating both blades 24 and 34 has a rotation center axis O of the first blade.
_It is a cylindrical surface centered on ₁ . In contrast, the first
The blade 24 has a scroll shape in which a plurality of arcs are combined, but as shown in FIG. 5, originally, a large diameter portion 24a 'which is an arc portion which is located at the outermost radial direction.
(The mesh portion outside the radius Ro in the figure) is deleted, and the outer end portion of the remaining portion is in an arc shape slidable on the housing inner peripheral surface 10a (specifically, the rotation center O ₁ is the center). The sliding surface 24a has a circular arc shape, and the labyrinth seal portion 24b having a plurality of grooves is formed on the sliding surface 24a.
Is recessed. That is, the inner peripheral surface 1 of the central housing
0a is also used as the inner peripheral surface of the large-diameter portion 24a 'removed as described above. On the other hand, the second
Similar to the first blade 24, the blade 34 also has a scroll shape in which a plurality of arcs are combined.
Is arranged on the inner side in the radial direction, and the outermost circular arc portion is a large diameter portion 34a having the central axis O ₂ of the second scroll member 20 as the circular arc center. The inner end portion of the second blade 34 is branched into two small diameter portions 34b and 34c, and a discharge port 35 is formed between the small diameter portions 34b and 34c. The discharge port 35 corresponds to the cylindrical portion 36. It communicates with the inner space in the axial direction. The radius R1 of the inner peripheral surface 10a of the central housing is the sum (R2 +) of the outer radius R2 of the large diameter portion 34a and the eccentricity e of the central axes O ₁ and O _2.
e) and the sliding surface 24 of the arc shape
The radius Ro of the circumscribed circle centering on the center O _{1 of a} is also
It is set equal to this sum (R2 + e). The eccentricity e of the central axes O ₁ and O ₂ is determined by the inner peripheral surface 10 of the housing.
The difference between the inner diameter R1 of a and the outer diameter R2 of the large diameter portion 34a (R
1-R2).

The second side wall 32 is formed in a shape substantially equal to the circumscribed circle of the second blade 34 centered on the central axis O ₂ (that is, a circular shape slightly smaller than the first side wall 22). . On the other hand, the side wall housing 14 has a recess 1
4a is formed, and the shape thereof is substantially the same as the circumscribed circle of the second blade 34 centered on the central axis O ₂ and the second side wall 32 can be fitted into the circular shape.
The second side wall 32 is rotatably fitted in the recess 14a. The first side wall 22 covers the entire axial end (left end in FIG. 2) of the working chamber formed between the blades 24 and 34 as described later, while the second side wall 22 is formed.
The side wall 32 covers only a part of the other axial end (the right end in FIG. 2) of the working chamber, and the other portion (that is, a portion radially outer than the second side wall 32) is the side wall housing 14. Both scroll members 1 so that they are directly covered
8 and 20 are arranged.

Next, the connecting structure between the scroll members 18 and 20 will be described. In the peripheral portion of the first side wall 22,
A disk-shaped link plate 46 is rotatably held around a center axis O _{4 of} the circle via a bearing 44, and the link plate 46 is parallel to the center axes O ₁ and O ₂ via a bearing 47. A connecting shaft 48 extending in the direction is held rotatably around its central axis O ₃ . On the other hand, a shaft engaging portion 34d having a larger wall thickness than other portions is formed at an intermediate portion of the second blade 34 of the second scroll member 20, and the shaft engaging portion 34d is opened toward the connecting shaft 48. A hole 49 is formed therein, and the connecting shaft 48 is inserted into the hole 49. Here, the central axis O ₃ is eccentric from the central axis O ₄ by an amount equal to the eccentricity e of the central axes O ₁ and O ₂ , and the eccentric direction of the central axes O ₃ and O ₄ is the central axis O 3. The positions of the holes 49 are set so as to be parallel to the eccentric directions of ₁ and O ₂ .

Therefore, a link mechanism (parallel crank mechanism) having a pair of turns about the central axes O _{1 to} O ₄ with the entire housing, the first scroll member 18, the second scroll member 20, and the link plate 46 as nodes is constituted. 1 and FIGS. 6 to 9 show a parallelogram O ₁ indicated by a broken line.
O ₂ O ₃ O ₄ ).

A one-way clutch (one-way clutch) 50 is provided between the outer peripheral surface of the cylindrical portion 36 and the inner surface of the side wall housing 14, and the one-way clutch 50 is provided.
Thus, the reverse rotation of the second scroll member 20 (the rotation in the direction opposite to the rotation direction of the first scroll member) is restricted.

Next, the operation of this scroll type compressor will be described.

When the rotary drive source connected to the pulley 30 is operated, the entire first scroll member 18 is rotationally driven around the central axis O ₁ , and the sliding surface 24a at the end thereof is driven.
Slides on the inner peripheral surface 10a of the housing. With this rotational drive, the second scroll member 20 connected to the first scroll member 18 via the connecting shaft 48 is also simultaneously driven to rotate about the central axis O ₂ at the same angular velocity as the first scroll member 18. Will be.

By the interlocked rotation in such an eccentric state,
First, as shown in FIG. 6, when the outer surface of the large-diameter portion 34a of the second blade 34 starts to come into contact with the housing inner peripheral surface 10a at a point P2, the area surrounded by both blades 24, 34 and the housing inner peripheral surface 10a. The contact point P2, the contact point P1 between the tip of the sliding surface 24a and the inner peripheral surface 10a of the housing, and the first blade 2
4 an outer working chamber 33A closed by a contact point P3 between the inner surface and the outer peripheral surface of the second blade 34 is formed.
The fluid sucked from the suction port 21 is sealed in 3A. That is, the housing inner peripheral surface 10a
Plays the same role as the inner peripheral surface of the removed portion (large diameter portion 24a ') of the first blade 24 shown in FIG. 5, and the outer working chamber 33A is formed between the second blade large diameter portion 34a. Form.
From this state, when the scroll members 18, 20 rotate 90 ° clockwise in FIG. 6 to reach the state shown in FIG. 7, the volume of the outer working chamber 33A becomes smaller than the volume in the state shown in FIG. The fluid in the outer working chamber 33A is compressed accordingly.

When it further rotates 90 ° to the state shown in FIG. 8, the volume of the outer working chamber 33A decreases more and more, and the pressure inside the outer working chamber 33A becomes higher. On the other hand, the second blade 34
The outer surface of the first blade 24 makes contact with the inner surface of the first blade 24 at a point P5, and the inner working chamber 33B closed by the contact point P5 and the contact point P4 between the inner end portions of the two blades 24 and 34 is the both blade 24. ，
It begins to form during 34. Further rotate 90 °
In the state shown in (1), the contact point P2 catches up with the contact point P1, and the outer surface of the second blade 34 starts to contact the inner surface of the outer end portion of the first blade 24. At this point, the outer working chamber 3
3A becomes the maximum pressure, and immediately thereafter, it is opened to the discharge port 35, and the fluid trapped in the outer working chamber 33A is discharged from the discharge port 35 to the outside of the compressor through the cylindrical portion 36 and the discharge port 38 under high pressure. To be done. On the other hand, the compression of the fluid is started in the inner working chamber 33B. By further rotating the state of FIG. 9 by 90 ° in this way, the state shown in FIG. 6 is restored, and thereafter, the same suction and discharge as described above are repeated.

During such rotation, the central axes O _{1 to} O _{4 are}
The second scroll member 20 can theoretically rotate both in the same direction as the previous rotation direction and in the opposite direction at the moment when the lines are aligned.
Reverse rotation of the scroll member 20 is prevented by the one-way clutch 50.

As described above, in this compressor, the large diameter portion 2 of the first blade 24, which is originally required to form the outer working chamber 33A, is used.
4a 'is deleted, and the outer end portion (sliding surface 24a) of the remaining portion of the first blade 24 is replaced with the housing inner peripheral surface 1 instead.
Since the housing inner peripheral surface 10a is also used as the inner peripheral surface of the large diameter portion 24a 'by sliding on 0a, the large diameter portion 24a is secured while ensuring a sufficient fluid suction amount.
The elimination of a'can reduce the size and weight of the first blade 24 and the central housing 10 that houses it.

Particularly, in this embodiment, the outer end portion has an arcuate sliding surface 24a along the inner peripheral surface 10a of the housing.
Since the sliding surface 24a is brought into surface contact with the housing inner peripheral surface 10a and the labyrinth seal portion 24b is formed on the sliding surface 24a, for example, the outer end portion and the housing inner peripheral surface 10a are It is possible to further improve the sealing property in the sliding portion as compared with the structure in which line contact (point contact when viewed from the front) is performed.

Further, in this embodiment, when the inner end portions of both blades 24 and 34 contact each other at a point P4 as shown in FIG. 8, and then the contact point P2 reaches P1 as shown in FIG. That is, after a lapse of time when the outer side surface of the second blade 34 begins to come into contact with the inner side surface of the first blade 24, as shown in FIG.
Since the shapes of 4 and 34 are set, the contact point P1 between the sliding surface 24a and the housing inner peripheral surface 10a is always separated from the discharge port 35 by the contact point P3. Therefore, it is possible to avoid the high pressure of the fluid discharge pressure from directly acting on the contact point P1, and it is possible to prevent the inconvenience that the fluid easily leaks from the sliding portion of the sliding surface 24a by the high pressure action.

Next, a second embodiment will be described with reference to FIGS.

In the above embodiment, the fluid is sucked into the working chamber between the blades 24 and 34 from the axial direction.
In this embodiment, the suction port 15 is formed in a part of the inner peripheral surface 10a of the central housing in the circumferential direction.
A suction port 16 is formed in the central housing 10 for sucking the fluid in the radial direction.

Here, the suction port 15 has a width of an angle α in the circumferential direction of rotation. The starting point (both wings 2
The position of the upstream end point (Q4) of 4, 34 is the second position.
It is set at a position equivalent to the contact point P2 between the outer surface of the blade outer diameter portion 34a and the housing inner peripheral surface 10a, and the position of the end point (end point on the downstream side in the rotation direction) Q2 is as shown in FIG. When the outer surface of the second blade outer diameter portion 34a and the housing inner peripheral surface 10a start contacting with each other at the contact point P2, the contact point P1 between the housing inner peripheral surface 10a and the tip of the sliding surface 24a reaches. Set to the position.

According to such a compressor, in the state shown in FIG. 12, the outer working chamber 3 extends from the suction port 16 and the suction port 15 through the outer ends of the blades 24 and 34.
The fluid can be sucked into the inside of 3A from the radial direction, and thereafter, with the rotation of both blades 24 and 34 as shown in FIGS. 13 to 17, the compression and discharge of the fluid are performed as in the first embodiment. Can be performed continuously. Moreover, the start point Q1 of the suction port 15 is at the same position as the contact point P2, and the end point Q2 is at the same position as the arrival position P1 of the sliding surface 24a at the contact start point at the contact point P2. Therefore, in the state shown in FIG. 12, it is possible to secure the maximum opening area of the suction port 15 while securing the airtight inside the outer working chamber 33A.

In this embodiment, the starting point Q
The position 1 may be set on the downstream side in the rotation direction (on the right side in FIG. 12) with respect to the contact point P2 in order to secure the sealing property more reliably. Further, the position of the terminal point Q2 may be slightly deviated from the arrival position P1 of the sliding surface 24a at the time of starting the contact to the upstream side or the downstream side in the rotation direction without any problem.

Next, a third embodiment will be described with reference to FIGS.

In each of the above embodiments, the radius R1 of the inner peripheral surface 10a of the central housing and the radius Ro of the circumscribed circle of the arcuate sliding surface 24a of the first blade 24 are both the same as those of the second blade. It is set equal to the sum (R2 + e) of the outer radius R2 of the large diameter portion 34a and the eccentric amount e of the central axes O ₁ and O ₂ , but in the third embodiment, the radii R1 and Ro are set.
Are set to be smaller than the sum (R2 + e), and the housing inner peripheral surface 10
a has a _second radius of curvature R2 centered on the central axis O 2.
The arcuate surface 10b is recessed in the eccentric direction (upward in FIGS. 18 and 19). That is, this second arc surface 1
0b is formed in a region between the points P21 and P22 that sandwich the contact point P2 shown in the first embodiment in the center (region of angle θ1 shown in FIG. 18).

According to this structure, the outer peripheral surface of the second blade large-diameter portion 34a makes surface contact with the housing inner peripheral surface 10a over the entire area of the second arc surface 10b (that is, the area of points P21 to P22). , The structure shown in the first embodiment, that is, the second blade large-diameter portion 3 having the radius of curvature R2.
4a outer peripheral surface and housing inner peripheral surface 1 having a radius of curvature R1
Compared with the structure in which 0a is in direct line contact, there is an advantage that the fluid leakage resistance at this contact portion can be increased and the sealing property can be further improved.

In this structure, as shown in FIG. 20, when the sliding surface 24a of the first blade 24 passes over the second arc surface 10b, a minute gap 60 is formed between the two surfaces 24a, 10b.
However, since the outer working chamber 33A as shown in FIG. 18 is not yet formed at this point, even if the gap 60 is formed, the hermeticity of the outer working chamber 33A is not adversely affected. Even if the shapes of both blades 24 and 34 are set so that a closed working chamber is formed when the first blade 24 passes over the second arc surface 10b,
As shown in FIG. 21, if the radius R1 of the inner peripheral surface 10a of the central housing is suppressed so that the angular width θ1 of the second arc surface 10b in the circumferential direction becomes smaller than the angular width θ2 of the sliding surface 24a, At the time of passage, the entire second arc surface 10b can be completely covered by the sliding surface 24a, so that the working chamber can be hermetically sealed.

Further, the present invention can also adopt the following aspects.

(1) In the above embodiment, both scroll members 1
8 and 20 are connected by the connecting shaft 48, and both are driven in conjunction with each other, but the scroll compressor of the present invention is not limited to this, and both scroll members 18 and 20 may be individually driven to rotate. Good.

(2) In the present invention, the shape of each of the blades 24, 34 may be set as appropriate, and may be a combination of a plurality of arcs as described above, or an involute curve. Further, the discharge port 35 may be formed not on the second scroll member 20 side but on the first scroll member 18 side.

(3) In the third embodiment described above, the compressor in which the fluid is sucked in the radial direction has the second arc surface 10b formed, but as shown in the first embodiment, the fluid is axially moved. Similarly, in the compressor sucked into the second arc surface 1
By forming 0b, it is possible to obtain the effect of improving the sealing property.

[0051]

As described above, according to the present invention, originally, the radially outer portion of the first blade, which is necessary for forming the working chamber, is deleted, and instead, the outer end portion of the remaining portion of the first blade is cylindrical. Since the inner peripheral surface of the housing is also used as the inner peripheral surface of the deleted portion by sliding on the inner peripheral surface of the housing, the first portion can be secured while ensuring a sufficient fluid suction amount. There is an effect that the first blade and the housing for housing the first blade can be made smaller and lighter by partially removing the blade.

Particularly, in the compressor according to the second aspect, the outer end portion is formed into an arcuate sliding surface along the inner peripheral surface of the housing, and the sliding surface is brought into surface contact with the inner peripheral surface of the housing. Since the labyrinth seal portion is formed on the sliding surface, the sealing performance at the sliding portion can be improved as compared with, for example, a structure in which the outer end portion and the housing inner peripheral surface are in line contact (point contact when viewed from the front). There is an effect that can be further enhanced.

Further, in the compressor according to the third aspect of the present invention, after the inner end portions of both blades contact each other and a time point after which the outer surface of the second blade begins to contact the inner surface of the first blade, Since the shape of both blades is set so that the inner end portions are separated from each other, the contact point between the sliding surface and the inner peripheral surface of the housing can be always isolated from the central discharge port by the contact between both blades. Accordingly, there is an effect that it is possible to prevent the inconvenience that the high fluid discharge pressure directly acts on the contact point and the fluid easily leaks from the sliding portion of the sliding surface.

In the compressor according to the fourth aspect, the fluid can be axially sucked into the working chamber between the two blades through the suction port provided on the side wall covering one end of the first blade without any trouble.

On the other hand, in the compressor according to claim 5,
A fluid can be sucked into the working chamber from the radial direction through a suction port opened in a part of the inner circumferential surface of the housing in the circumferential direction. Moreover, one end of the suction port is located at a contact point between the outer surface of the second blade and the inner circumferential surface of the housing or at a position downstream of the contact point in the rotational direction of both scroll members, and the other end of the suction port is located. Is substantially the same as the position where the sliding portion of the first blade reaches at the time when the outer surface of the second blade and the inner peripheral surface of the housing start to contact. After a short time, it is possible to reliably isolate the working chamber formed between the two blades from the suction port, thus maintaining the compression efficiency of the fluid in the working chamber high, and There is an effect that a large suction port opening area can be secured and thus a larger fluid suction amount can be secured.

In the compressor according to the sixth aspect, both the radius of the inner peripheral surface of the housing and the radius of the circumscribed circle of the sliding portion of the first blade about the rotation center of the first scroll member are both set. , The radius of the circumscribed circle of the second blade and the first
The second blade is set to be smaller than the sum of the eccentric amounts of the rotation center axis of the scroll member and the rotation center axis of the second scroll member, and the rotation center axis of the second scroll member is centered on the inner peripheral surface of the housing. Since the second arcuate surface having a radius of curvature equal to the radius of the circumscribed circle is recessed in the eccentric direction of the both rotation center axes, the outer circumference of the second blade protruding from the circumscribed circle of the first blade by the above setting. A structure in which the outer surface of the second blade is in line contact with the inner peripheral surface of the housing having a larger radius of curvature than the outer peripheral surface by bringing the surface into surface contact with the second arc surface having the same radius of curvature as the outer peripheral surface. Compared with the above, there is an effect that the sealing property at the contact portion can be further enhanced and the compression efficiency can be further enhanced.

Here, in the compressor according to the seventh aspect, since the central angle of the second arc surface is set to be smaller than the circumferential angular width of the sliding portion of the first blade, When the sliding portion passes over the second circular arc surface, the second circular arc surface can be completely covered with the sliding portion, and thus the blade shape is formed so that the working chamber is formed during this passage. Even when is set, there is an effect that the airtightness in the working chamber can be ensured satisfactorily.

[Brief description of drawings]

FIG. 1 is a cross-sectional view of a scroll compressor according to an embodiment of the present invention, which is a cross-sectional view taken along the line AA of FIG.

FIG. 2 is a sectional view taken along line BB of FIG.

3A is a sectional view taken along line DD of FIG. 3B, and FIG. 3B is a partial sectional side view of a first scroll member in the scroll compressor.

4A is a sectional view taken along line FF of FIG. 4B, FIG. 4B is a sectional side view of a first scroll member of the scroll compressor, and is a sectional view taken along line EE of FIG. Is.

FIG. 5 is a sectional front view showing a shape of a first blade of the first scroll member.

FIG. 6 is a cross-sectional view for explaining the operation of the scroll compressor.

FIG. 7 is a cross-sectional view for explaining the operation of the scroll compressor.

FIG. 8 is a cross-sectional view for explaining the operation of the scroll compressor.

FIG. 9 is a cross-sectional view for explaining the operation of the scroll compressor.

FIG. 10 is a sectional front view of the scroll compressor according to the second embodiment of the present invention, which is a sectional view taken along the line GG of FIG.

11 is a sectional view taken along line HH of FIG.

FIG. 12 is a cross-sectional view for explaining the operation of the scroll compressor.

FIG. 13 is a cross-sectional view for explaining the operation of the scroll compressor.

FIG. 14 is a cross-sectional view for explaining the operation of the scroll compressor.

FIG. 15 is a cross-sectional view for explaining the operation of the scroll compressor.

FIG. 16 is a cross-sectional view for explaining the operation of the scroll compressor.

FIG. 17 is a cross-sectional view for explaining the operation of the scroll compressor.

FIG. 18 is a sectional front view of a scroll type compressor according to a third embodiment of the present invention.

19 (a) is a front view of a central housing in the scroll compressor, and FIG. 19 (b) is a sectional view taken along line I-I of FIG. 19 (a).

FIG. 20 is a sectional front view showing a moment when the sliding surface passes over the second arc surface in the compressor.

FIG. 21 is a sectional front view showing a case where the angle width of the sliding surface is made larger than the angle width of the second arc surface in the third embodiment.

22 is a cross-sectional front view showing an example of a conventional scroll compressor, which is a cross-sectional view taken along the line JJ of FIG. 23.

23 is a sectional view taken along line KK of FIG.

FIG. 24 is a cross-sectional view for explaining the operation of the scroll compressor.

FIG. 25 is a cross-sectional view for explaining the operation of the scroll compressor.

FIG. 26 is a cross-sectional view for explaining the action of the scroll compressor.

[Explanation of symbols]

10 Central Housing 10a Central Housing Inner Surface 10b Second Arc Surface 15 Intake Port 16 Intake Port 18 First Scroll Member 20 Second Scroll Member 21 Intake Port 22 First Sidewall 24 First Blade 24a Sliding Surface 24b Labyrinth Seal Part 32 Second side wall 34 Second blade 35 Discharge port O ₁ Center of rotation of first scroll member O ₂ Center of rotation of second scroll member

Claims (7)

[Claims] 1. A first scroll member having a scroll-shaped first blade, a second scroll member having a second blade arranged inside the first blade, and the first scroll member and the second scroll member. And a housing for rotatably holding them at positions eccentric to each other, so that both scroll members rotate at equal angular velocities so that fluid is sucked into the working chamber between the two blades and discharged from the central portion. In the configured scroll compressor, an inner peripheral surface of a portion of the housing that accommodates both blades is a cylindrical surface, a radially outer portion of the first blade is partially removed, and an outer end portion of the remaining portion is formed. A sliding portion slidable over the entire inner peripheral surface of the housing is formed, and the working chamber is formed between the inner peripheral surface of the housing and the outer surface of the second blade. A scroll type compressor characterized in that 2. The scroll compressor according to claim 1, wherein an outer end surface of the first blade is an arcuate sliding surface along the inner peripheral surface of the housing, and a labyrinth seal portion is formed on the sliding surface. A scroll type compressor characterized in that. 3. The scroll compressor according to claim 1, wherein after the inner end portions of both blades contact each other, the inner surface of the outer end portion of the first blade contacts the outer surface of the second blade. After that, the shapes of the first blade and the second blade are set such that the inner end portions are separated from each other. 4. The scroll compressor according to claim 1, wherein the first scroll member is provided with a side wall that covers one axial end of the first blade, and an intake port is opened in the side wall. Then, the scroll compressor is configured to suck the fluid in the axial direction from the suction port into the working chamber. 5. The scroll compressor according to claim 1, wherein a suction port for sucking fluid from a radial direction is opened in a part of the inner peripheral surface of the housing in the circumferential direction, The position of one end of the suction port in the axial direction is set at the contact point between the outer surface of the second blade and the inner peripheral surface of the housing or at a position downstream of the contact point in the rotational direction of both scroll members, The scroll type, wherein the position of the other end is set to a position substantially equal to the position reached by the sliding portion of the first blade when the outer surface of the second blade starts to contact the inner peripheral surface of the housing. Compressor. 6. The scroll compressor according to claim 1, wherein the first blade is slid about a radius of the inner peripheral surface of the housing and a rotation center of the first scroll member. The radius of the circumscribed circle of each part is smaller than the sum of the radius of the circumscribed circle of the second blade and the eccentric amount of the rotation center axis of the first scroll member and the rotation center axis of the second scroll member. A second circular arc surface having a radius of curvature equal to the radius of the circumscribing circle of the second blade about the rotation center axis of the second scroll member is provided on the inner peripheral surface of the housing and is eccentric to both rotation center axes. A scroll compressor characterized by being recessed in the direction. 7. The scroll type compressor according to claim 6, wherein the inner circumference of the housing is such that the central angle of the second arc surface is smaller than the angular width of the sliding portion of the first blade in the circumferential direction. A scroll compressor characterized in that a radius of a surface and a circumferential width of a circumscribed circle of a sliding portion of the first blade centered on a rotation center of the first scroll member are set.