JPH0133675B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a compressor for an air conditioner, and in particular, a pair of spiral bodies are engaged with each other at different angles, and one spiral body is given relative circular motion (only orbital motion). The present invention relates to a refrigerant compressor called a scroll type in which compressed gas is discharged from the center by moving a closed space formed between both spiral bodies toward the center while decreasing the volume.

In the case of general indoor air conditioning, once the indoor temperature reaches the set temperature, only a small amount of refrigeration capacity is needed to compensate for the subsequent rise in indoor temperature. However, since air conditioners are normally turned on and off according to the indoor temperature or the temperature difference between indoor and outdoor,
After the room has been cooled to the set temperature, the more sensitive the device is, the more the device turns on and off, and a large load is intermittently applied to the drive source. In addition to the above-mentioned temperature problems, especially in the case of automobile air-conditioning systems, the refrigerant compressor is now driven by the automobile engine whose rotational speed changes from moment to moment. In order to avoid unnecessary drive, the electromagnetic clutch that connects and disconnects power transmission between the engine and compressor must be turned on and off frequently, and the load on the engine changes each time, so there are limits to its application to small cars. be.

Therefore, there is a need for a compressor that can reduce the compression ratio as necessary to lighten the load on the drive source without causing a large waste of energy consumption.

In a scroll type compressor, it is possible to vary the compression ratio by reducing the initial volume of the sealed space formed between both spiral bodies.

located closer to the center along the spiral than the normal fluid intake formed between the outer end of the spiral and the opposing outer wall of the spiral as a configuration that reduces the initial volume of the enclosed space. That is, one fluid passage hole is provided in the angular range from the outer end of the spiral (φ _eod in expansion/opening angle) to 2π toward the center (φ ₁ satisfying φ _eod > φ ₁ > φ _eod −2π), The present inventors have specifically proposed that another fluid hole is provided at a position (φ ₁ - π) shifted toward the center by π from the fluid hole, and that the opening and closing of the pair of fluid holes is controlled by a valve. It was proposed in 1983-33646.

However, the configuration disclosed in Japanese Patent Application No. 56-33646 has the disadvantage that the compressed volume cannot be reduced to a large extent when the valve is opened.

In order to increase the reduction in compressed volume, the fluid hole should not be located at the position determined by φ ₁ that satisfies φ _eod > φ ₁ > φ _eod −2π as described above, but should be located further inside than φ _{eod −2π} . It soon became clear that all you had to do was choose.

In this way, if φ ₁ is chosen to be inside φ _eod −2π, the resulting increase or decrease in the amount of fluid discharged from the scroll compressor will be greater than that of the conventional one, and the significance of this will be It was a success. However, as a result of careful consideration of the compression process when reducing the compression capacity in this case, the inventor found that after compressing the fluid once within the closed space formed outside the fluid passage, It was discovered that the fluid is discharged from the fluid hole that is taken in. In other words, the inventor has found that a scroll compressor in which φ ₁ is set to be inside φ _eod −2π has the disadvantage that unnecessary compression is performed to change the amount of compressed solubility. elucidated for the first time. Moreover, this wasteful compression causes the inconvenience that the power for driving the compressor is wasted.

Therefore, an object of the present invention is to provide a scroll type compressor that can reduce the volume by a large amount without performing unnecessary compression work.

That is, the present invention provides a movable scroll member in which a spiral body is disposed on one surface of a plate, and a fixed scroll member in which a spiral body is similarly disposed on one surface of a plate. The movable scroll member is arranged so that the angles are shifted and both spiral bodies are in contact, and the movable scroll member is revolved on a circular orbit to form a plurality of closed spaces between both spiral bodies. Fluid is taken in from the suction chamber at the outer end of the body, and as the movable scroll member moves, the fluid is moved around the closed space, and the volume is reduced to perform a unidirectional fluid compression action. In a scroll compressor, when the position on the spiral expansion line along the wall center of the spiral body of the fixed scroll is defined by the expansion angle φ, the outside of the spiral body is practically determined by the final expansion angle φ _eod . n (n is a positive integer of 2 or more) is provided on the plate of the fixed scroll member in order to communicate the sealed space with the suction chamber at a position closer to the center than the terminal end along the spiral direction. ) pairs of fluid holes and a valve that can open and close the n pairs of fluid holes, the two fluid holes constituting each pair are shifted from each other by π in the expansion/opening angle, and the n pairs of fluid holes are The position of the first pair of fluid holes that is the innermost pair of fluid holes is φ _eod −2(n−
1) The extension angle position φ ₁ satisfying π>φ1>φ _eod −2nπ is near the inner wall of the fixed spiral, and the paired hole is located at the position of φ ₁ ′=φ ₁ −π. It is provided near the outer wall of the body, and in general, the position of the k-th pair of fluid passage holes that is π outside in terms of expansion and opening angle is φ _k-1 +2〓＞φ _k ＞
φ _k+1 −2π (where φ _k-1 and φ _k+1 are (k-1)
In the th pair and the (k+1)th pair, the expansion angle is at the inner wall of the fixed spiral body at the expansion angle position φ _k that satisfies the position of the hole outside by π, respectively. The pair of resistors are provided on the outer wall of the fixed spiral wound body at the position φ _k ′ = φ _k −π, and the position of one of the outermost n-th pair of fluid passage holes is φ _o-1
+2π＞φ _o ＞φ _eod −2π (here, φ _o-1 is (n-1)
The expansion angle position φ _o that satisfies the position of the hole that is outside by π in the expansion angle of the second pair is near the inner wall of the fixed spiral body, and the hole in the pair is φ _o ′ = φ This scroll type compressor is characterized in that it is provided near the outer wall of the fixed spiral wound body at a position of _o - π.

Hereinafter, the present invention will be explained in detail with reference to embodiments shown in the drawings.

Referring to FIG. 1, the illustrated compressor 1 has a compressor housing 10 consisting of a front end plate 11 made of aluminum or an aluminum alloy, and a cup-shaped portion 12 installed on the front end plate 11.
have.

The front end plate 11 is formed around a through hole 111 through which the main shaft 13 is inserted, and an annular projection 112 concentric with the through hole 111 is formed on the back surface. On the other hand, the cup-shaped part 1
2 is formed by drawing a steel plate or by aluminum die casting. Cup-shaped part 12
is fitted and fixed onto the annular projection 112 of the opening front end plate. Note that an O-ring 14 is clamped at the joint to provide sealing.

A disk rotor 15 is fixed to the inner end of the main shaft 13, and this disk rotor 15 has a through hole 1.
It is rotatably supported within 11 by a ball bearing 16.

The front end plate 11 also has a main shaft 1.
It has a sleeve 17 that extends forward so as to surround 3. The sleeve 17 may be formed integrally with the front end plate 11, but here it is formed of steel separately from the front end plate, and is attached to the front surface of the front end plate 11 with screws 18. There is. A ball bearing 19 is located at the front end inside the sleeve 17.
is installed and rotatably supports the main shaft 13. Shaft seal assembly 20 is assembled on main shaft 13 within sleeve 17 .

On the outer surface of the sleeve 17, a pulley 22 is rotatably supported by a bearing 21, and an electromagnet 23 is fixed. On the other hand, on the end of the main shaft 13 protruding from the sleeve 17,
Armature plate 24 is elastically supported.
That is, the pulley 22, the electromagnet 23, and the armature plate 24 constitute an electromagnetic clutch, whereby the rotation of an external drive source (for example, an automobile engine) is transmitted to the pulley 2 through a belt.
By energizing the electromagnet 23, the armature plate 24 is attracted to the pulley 22, thereby transmitting the rotational force to the main shaft 13.

A fixed scroll member 25, a movable scroll member 26, a movable scroll drive mechanism 27, and a movable scroll rotation prevention mechanism 28 are provided in the cup-shaped portion 12 whose opening is closed by the front end plate 11.

The fixed scroll member 25 generally has a side plate 251
and a spiral body 252 fixed to one side thereof.A cylindrical partition wall 253 is formed on the back surface of the side plate 251 to protrude in the axial direction. It is fixed to the cup-shaped part 12 by suitable attachment means. Also side plate 2
A groove is formed on the outer peripheral surface of 51, and in this groove,
A seal ring 31 is arranged to seal between the outer peripheral surface of the side plate 251 and the inner surface of the cup-shaped portion 12. Therefore, the side plate 2 of the fixed scroll member 25
51, the inside of the cup-shaped portion is connected to the partition wall 25.
The chamber 32 is separated into a rear chamber 32 where the spiral body 3 is located, and a front chamber 33 where the spiral body 252 is located, and the chamber 32 is separated by a partition wall 253 into a suction chamber 36 and a discharge chamber 321.

A movable scroll member 26 is arranged within the chamber 33 . The movable scroll member 26 has a side plate 26
1 and a spiral body 262 fixed to one side thereof, the spiral body 262 is intertwined with the spiral body 252 with an angular deviation of 180 degrees, and a sealed space is formed between the two spiral bodies. . Movable scroll member 26
A radial bearing 27 is mounted on a drive wheel 271 eccentrically connected to the inner end surface of the disc rotor 15.
It is rotatably installed via 2. on the other hand,
A fixed ring 281 fixedly connected to the front end plate 11, a movable ring 282 fixed to the side plate 261 of the movable scroll 26 so as to face this, and ball receiving holes 28 formed in both rings.
The rotation prevention mechanism 28 is constituted by the balls 285 arranged in the 3,284.

The compressor housing 10 has a suction port 34 in the cup-shaped portion 12 for connection to an external fluid circuit.
and a discharge port 35. Suction port 34
The fluid introduced into the suction chamber 36 in the housing is further led to the chamber 33 through a through hole (not shown), taken into the sealed space between the scroll members 25 and 26, and is drawn into the circular motion of the movable scroll 26. It moves to the center while being compressed by the orbital motion, and enters the discharge chamber 3 through the discharge hole 254 provided in the center of the side plate 251 of the fixed scroll member 25 via the discharge valve 37.
21 and thence through discharge port 35 into the fluid circuit.

By the way, the intake of fluid into the closed space between both scroll members 25 and 26 is normally achieved through a total of two channels formed between the outer end of one spiral body 252 or 262 and the outer surface of the other spiral body. This is done through the fluid intake. That is, the fluid intake port is opened and closed according to the circular orbit movement of the movable scroll member 25, and at that time both scroll members 25,
The fluid is taken into the sealed space between 26. Here, since the positions of the outer ends of the spiral bodies 252 and 262 are expressed by the final expansion/opening angle φend, the position of the fluid intake port is also determined automatically by the final expansion/opening angle φend.

Furthermore, with reference to FIG. 2, an embodiment in which two pairs of fluid passage holes are provided will be described.
exceeds 4π, and the four fluid holes 255, 256, 258, 259 communicating with the chamber 36
have.

The fluid passage hole 255 corresponds to a position of a certain extension angle φ ₁ of the spiral body 252 and is provided so as to open inside the spiral body 252 . Fluid hole 25
Reference numeral 6 corresponds to a position of a certain expansion/opening angle (φ ₁ −π) of the spiral body 252 and is provided so as to open to the outside of the spiral body 252 . Therefore, the fluid passage holes 255 and 256 are both connected to the outermost end of the spiral of the fixed scroll member, the outer wall of the spiral of the movable scroll member, and the outermost end of the spiral of the movable scroll member to the spiral of the fixed scroll member. Provided at a position closer to the center along the spiral direction than the fluid intake ports (two locations) formed between the outer walls of the roll,
Both fluid passages 255, 256 are simultaneously closed by the spiral bodies of the opposing movable scroll members.
Here, the φ ₁ that defines the angular position where the fluid passage holes 255 and 256 are provided is selected within the range determined by φ _eod −2π>φ ₁ >φ _eod −4π (1).

Next, the fluid passage hole 258 is provided so as to correspond to a position of a certain expansion/opening angle φ ₂ of the spiral body and to open on the inner wall side of the spiral body 252 . Further, the fluid passage hole 259 has a certain extension angle (φ ₂
-π) and is provided so as to open on the outer wall side of the spiral body 252. Here, the φ ₂ that defines the angular position at which the fluid passage holes 258 and 259 are provided is selected within the range determined by φ ₁ +2π>φ ₂ >φ _eod −2π.

Therefore, both fluid passages 258, 259 are located on the outside along the spiral direction from the previously provided fluid passage holes 255, 256, and closer to the center along the spiral direction than the fluid intake port. located at the location.

Here, fluid holes 255, 256, 258, 25
9 is generally formed on the side plate 251 of the fixed scroll member 25 from the side opposite to the spiral body 252 using a drill. At that time, one fluid passage hole 25
5, 258 is located at a position slightly recessed into the inner wall surface of the spiral wound body 252, and the other fluid passage hole 256, 25
9 are formed at positions slightly recessed into the outer wall surface of the spiral wound body 252, so that the cross-sectional area of the through holes can be increased. Thereby, when the fluid passage hole is opened, the fluid sufficiently flows out through the fluid passage hole, thereby preventing compression from occurring. Note that the fluid passage hole 25
5, 256, 258, and 259, as can be seen from FIG. In order to prevent abrasion of the tip seal 38 due to interference between the tip seal 38 disposed at the tip of the spiral wound body 262 and the fluid passage hole even when the tip seal 38 is moved to a certain position, the diameter is set so that the tip seal 38 does not come into contact with the tip seal 38. In addition, if sufficient sealing performance can be maintained even without a tip seal, or if the tip seal has sufficient wear resistance, the fluid passage can be provided in a space on the opposite side even when covered by the opposing spiral body 262. The diameter may be such that it does not communicate with 39.

In addition, as shown in FIGS. 4 and 5, each fluid passage hole (255 is shown as an example) may be provided near the side wall of the spiral body. Even in this case, the diameter is assumed to be as described above.

Each of the fluid passage holes 255, 256, 258, and 259 may be formed by forming a plurality of them adjacent to each other along the spiral direction, or by integrating the plurality of holes to form a long hole, thereby increasing the cross-sectional area. You can also measure

Fluid holes 255, 2 are provided on the side plate 251 of the fixed scroll member 25 opposite to the spiral body 252.
The plate-shaped valves 41 are fixed in one-to-one correspondence to the valves 56, 258, and 259 using fixing means 42 such as screws. These plate-shaped valves 41 are made of a resilient ferromagnetic material, and normally press against the side plate 251 to open the fluid passages 255, 256, 258, 2.
59 is closed, but when a ring-shaped electromagnet 43 as shown in FIG. 255, 25
6,258,259. The electromagnet 43 is attached here by fitting it into a groove 257 provided on the outer periphery of the partition wall 253 and using a snap spring 44 as shown in FIG. 7, but it is possible to make various modifications. Not even. Note that the valve 41 has fluid holes 255, 256,
It is better to provide a portion that fits into these fluid passage holes when 258 and 259 are closed. This results in
Since each fluid passage hole is filled when the valve 41 is closed, there is an advantage that no re-expansion volume is generated.

In the configuration as described above, the fluid passage hole 25
When the movable scroll member 26 is driven in a predetermined manner with the electromagnets 5, 256, 258, and 259 closed, that is, with the electromagnet 43 in a non-energized state, fluid is supplied to both the spiral bodies 252, 262 from the fluid intake port described above.
The compressed fluid is taken into the space formed between them, and as the volume of the space decreases, the fluid is compressed and moved to the center, and the compressed fluid is discharged from the discharge hole 254 into the chamber 32 . At this time, since the initial volume of the sealed space formed between both spiral bodies 252 and 262 is large,
It has a high compression ratio and works as a high-capacity compressor.

In addition, the electromagnet 43 is energized to attract the valve 41 to the valve adsorption portion 431, and the fluid passage holes 255, 256, 2
When the movable scroll member is driven in the same manner with 58, 259 open, contact points A1 _{, A2} , and _B1 between both spiral bodies 252, 262, as shown in FIG.
As the movable scroll member moves, the fluid taken into the two outermost spaces a ₁ and b ₁ formed by B ₂ moves to the innermost point along the spiral body as the contact points A ₁ and B ₁ move. As shown in FIG. 8a, the fluid flows out from the fluid holes 258, 259 into the chamber 36 until the contact points A ₂ , B ₂ reach the fluid holes 255, 256 provided in the fluid holes 255, 256. 258 _, 259 _, as shown in FIG.
After reaching the fluid passages 255 and 256, as shown in FIG.
5,256 to chamber 36. As a result, while the spaces a ₁ and b ₁ between both spiral bodies 252 and 262 are in communication with the chamber 36 through the fluid passage holes 255, 256, 258, and 259, the fluid taken in cannot be compressed. do not have. and those spaces
When a ₁ and b ₁ move toward the center and are blocked from the fluid passages 255 and 256 as shown in FIG. 8d,
After that, the remaining fluid will be compressed. At this time, since the initial volume of the sealed space formed between both spiral-wound bodies 252 and 262 is small, the compression ratio is small and the compressor functions as a small-capacity compressor. As is clear from the above, fluid passage hole 25
5, 256, 258, 259, the closed spaces a ₁ and b ₁ are connected to the outer pair of fluid passage holes 258, 259.
In addition, compression does not start until passing through the inner pair of fluid holes 255 and 256, so as in the above-mentioned Japanese Patent Application No. 56-33646 (Japanese Unexamined Patent Publication No. 57-148089), The compression container can be made smaller than when only the holes 258 and 259 are provided, and unnecessary compression is not performed.

In this way, this scroll compressor can switch between large and small capacities by opening and closing the valve 41 as necessary, and no unnecessary compression work is performed when used at either capacity. . In addition, fluid passage holes 255, 256, 258, 25
In Figures 8a to 8d, which show the open state of the valve 9, the space that exerts a compressive action on the fluid is shaded.

Note that φ ₁ that defines the angular position where the fluid passage holes 255 and 256 are provided is selected within the range determined by the above equation (1), but in this case, if φ ₁ approaches (φ _eod −4π), The spaces a ₁ and b ₁ shown in FIG. 8c, ie, the containment volume, become smaller. Therefore, it is possible to make a large difference in capacity, but if φ ₁ is made smaller than (φ _eod −4π), unnecessary compression work will be performed.

Therefore, φ ₁ defining the angular positions φ ₁ , φ ₁ ′ (=φ ₁ −π) of the innermost pair of fluid passages is defined as φ _eod −4π＞
_φ1
>φ _eod −6π, according _to the _present invention, as _shown in FIG. φ ₃ and φ ₃ ′ (=φ ₃
-π), it is necessary to provide the outermost pair of fluid passages.

Here, φ ₂ and φ ₃ are selected so as to satisfy the following inequality.

φ ₁ +2π＞φ ₂ >φ ₃ −2π φ ₂ +2π＞φ ₃ >φ _eod −2π By doing this, when all the fluid holes are opened, the expansion is smaller than φ _eod −4π. Since compression does not start until the closed space passes a corner position, that is, a position closer to the center, the compression volume reduction ratio when all fluid holes are closed is larger than that of the embodiment shown in FIG. be able to.

Furthermore, when all the fluid holes are opened in the embodiment shown in FIG. 9, the compression operation is performed even in the closed space formed outside the innermost pair of fluid holes φ ₁ and φ ₁ −π. be exposed. However, since these sealed spaces communicate with the suction chamber through the fluid holes φ ₂ and φ ₂ -π and the fluid holes φ ₃ and φ ₃ -π, respectively, the compression of these sealed spaces Along with the operation, the fluid in the closed space flows through the fluid holes φ ₂ , φ ₂ −π,
Since the fluid is discharged into the suction chamber via φ ₃ and φ ₃ -π, no fluid compression actually takes place in these closed spaces. That is, wasteful fluid compression is not performed. Such actions and effects are caused by the fluid passages φ ₂ , φ ₂ −π and φ ₃ ,
Expansion/opening angular position of φ ₃ −π φ ₂ , φ ₂ −π and φ ₃ , φ ₃ −
This occurs only when π satisfies the above inequality, and when it does not satisfy the above inequality, unnecessary compression is performed.

In addition, in the case of the embodiment shown in FIG. 9, if only one pair of fluid holes φ ₃ and φ ₃ -π are opened, two pairs of fluid holes φ ₃ and φ ₃ -π and the fluid hole φ _{2 are} opened. , φ ₂ −π, or all three pairs of fluid holes φ ₃ , φ ₃ −π, fluid holes φ ₂ , φ ₂ −π, and fluid holes φ ₁ , φ ₁ −π 8, the compression capacity can be adjusted more finely than in the case of the embodiment shown in FIG. Therefore, the compression capacity of the scroll compressor can be made more fine and suitable for the operating conditions of the cooling device at that time.

As described above, in the present invention, the fixed scroll member of the scroll compressor is provided with n (n>2) pairs of fluid communication holes for communicating the sealed space between the movable and fixed scroll members with the suction chamber. ,
Letting the angular positions of the innermost pair of fluid holes be φ ₁ and φ ₁ ′ (=φ ₁ − π), φ ₁ becomes φ _eod −2(n−1)π>φ ₁ >φ _eod −2nπ , and the positions of the (k-1)th, kth, and (k+1)th fluid holes from this innermost pair of fluid holes to the outside are φ _k-1 and φ _k-1 '( =
φ _k-1 −π), φ _k and φ _k ′ (=φ _k −π), φ _k+1 and φ _k+1 ′ (=φ _k+1 −π), then this φ _k becomes φ _{k -1} +2π>φ _k >φ _k+1 −2π, and the positions of the outermost n-th pair of fluid holes φ _o , φ _o ′ (=φ _o −π) are φ _o-1 +2π ＞φ _o ＞φ _eo
d
−2π (where φ _o-1 is the position of the hole outside by π of the (n-1)th pair), so n pairs of fluid passages are formed between the pairs of scrolls. Of the fluid pockets forming the structure, each of the fluid pockets from the outside communicates with the nth pair of fluid pockets.Since valves are provided to open and close these fluid passage holes, the compression capacity can be increased or decreased in multiple stages by opening and closing the valves. By selecting n (n>2) according to the desired reduction in compression capacity,
This has the advantage that a desired reduction in the amount of compression can be achieved without unnecessary compression. Such actions and effects are produced only by selecting the angular position of each fluid passage so as to satisfy the above inequality. If the angular position of each fluid passage is not selected to satisfy the above inequality, fluid will be wasted in the closed space formed outside the open pair of fluid passages. This will cause power loss.

[Brief explanation of drawings]

FIG. 1 is a sectional view showing an embodiment of a scroll compressor according to the present invention, FIG. 2 is a front view of a fixed scroll member, FIG. 3 is a sectional view of only the portion provided with fluid holes, and FIG. 4 5 is a cross-sectional view showing another embodiment of the drilling position of the fluid hole, FIG. 6 is a perspective view of the electromagnet, FIG. 7 is a front view of the snap spring, and FIG.
Figure a is an explanatory diagram showing the moment when fluid is taken in by both spiral bodies, Figures 8 b, 8 c, and 8 d are explanatory diagrams showing a state in which the movable spiral body has further been driven; FIG. 9 is an explanatory diagram showing the positions of the communicating holes when n=3. 1... Compressor, 25... Fixed scroll member,
251... Side plate, 252... Spiral body, 254...
...Discharge hole, 255, 256, 258, 259...
Fluid hole, 26...Movable scroll member, 261
... Side plate, 262 ... Spiral body, 41 ... Valve, 4
3...Electromagnet.

Claims (1)

[Scope of Claims] 1. A movable scroll member with a spiral body disposed on one side of a plate, and a fixed scroll member with a spiral body similarly disposed on one side of the plate. The movable scroll member is arranged at different angles from each other and the side walls of both spiral winding bodies are in contact with each other, and the movable scroll member is caused to revolve on a circular orbit to form a plurality of closed spaces between both spiral winding bodies. Fluid is taken in from the suction chamber at the outer ends of both spiral bodies, and as the movable scroll member moves, the fluid is moved around the closed space, and the volume is reduced to perform a unidirectional fluid compression action. In the scroll type compressor, when the position on the spiral expansion line along the wall center of the spiral body of the fixed scroll is defined by the expansion angle φ, the final expansion angle φ _eod substantially determines the position. In order to communicate the sealed space to the suction chamber at a position closer to the center along the spiral direction than the outer end of the spiral body, n (n is 2 or more) is provided on the plate of the fixed scroll member. a positive integer) pairs of fluid holes, and a valve that can open and close the n pairs of fluid holes;
The two fluid holes constituting each pair are offset from each other by π in the expansion angle, and the first pair of fluid holes that is the innermost of the n pairs of fluid holes has an expansion angle of π. The position of the outer hole is φ _eod −2(n−1)π>
The extension angle position φ ₁ that satisfies φ ₁ > φ _eod −2nπ is near the inner wall of the fixed spiral body, and the paired hole is φ ₁ ′ = φ ₁ −
provided near the outer wall of the fixed spiral wound body at a position of π,
In general, of the kth pair of fluid passages, the extension angle is π
The position of the outer hole is φ _k-1 +2π>φ _k >φ _k+1 −2π
(Here, φ _k-1 and φ _k+1 indicate the position of the hole outside the expansion angle by π in the (k-1)-th pair and the (k+1)-th pair, respectively.) It is located near the inner wall of the fixed spiral body at the expansion/opening angle position φ _k , and the paired hole is provided near the outer wall of the fixed spiral body at the position φ _k ′=φ _k −π, and the outermost n The position of one hole in the second pair of fluid holes is φ _o-1 +2π>
φ _o > φ _eod −2π (here, φ _o ^- ₁ indicates the position of the hole outside the (n-1)th pair by π in terms of expansion and opening angle)
The expansion/opening angle position φ _o that satisfies is located near the inner wall of the fixed spiral wound body, and the paired hole is provided near the outer wall of the fixed spiral wound body at a position of φ _o ′=φ _o −π. A scroll compressor characterized by: 2. The scroll compressor according to claim 1, wherein the fluid passage hole is provided so as to be recessed into a side wall of the fixed spiral wound body. 3. The scroll mold according to claim 2, wherein the fluid passage is formed to reach the spiral body from a surface of the plate of the fixed scroll member opposite to the spiral body surface. compressor. 4. The scroll mold according to claim 2 or 3, wherein the diameter of the fluid passage hole is set to a size that does not contact the tip seal provided at the tip of the spiral body of the opposing movable scroll member. compressor. 5 The diameter of the fluid passage is such that even when the spiral body of the opposing movable scroll member moves to a position facing the fluid passage hole, it will not straddle the opposing spiral body and communicate with the space on the opposite side. A scroll type compressor according to claim 2 or 3, characterized in that the scroll compressor has a large size. 6. The scroll compressor according to claim 1, wherein the valve is positioned to face an outer end of the fluid passage. 7. The scroll compressor according to claim 6, wherein the valve has a portion that fits into the fluid hole when the fluid hole is closed.