JP2794863B2 - Variable capacity scroll compressor - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION [Industrial Application Field] The present invention is movable between a fixed scroll housed in a housing and a movable scroll provided so as to be non-rotatable and revolvable opposite to the fixed scroll. BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a scroll compressor that forms a closed space whose volume decreases based on the revolution of a scroll, and more particularly to a variable displacement scroll compressor characterized by a variable displacement mechanism.

[Prior Art] JP-A-61-291792 discloses a variable capacity scroll compressor.
As disclosed in Japanese Unexamined Patent Application Publication No. H11-163, a bypass hole is provided at a position closer to the inside than the outermost end of the spiral portion of the fixed scroll, and an intermediate pressure for communicating the bypass hole with the suction chamber via a check valve. A chamber (bypass chamber) is provided, and an opening / closing valve mechanism provided on an output side of the intermediate pressure chamber is operated to selectively connect the intermediate pressure chamber and the suction chamber to control the pressure of the intermediate pressure chamber. In this configuration, the check valve is opened and closed so that the compression capacity is increased when the on-off valve mechanism is closed. In this type of variable capacity mechanism, the bypass amount, that is, the capacity reduction amount, is regulated by the area of the bypass hole. To increase the bypass amount, the number of bypass holes needs to be increased, and a check valve is provided for each bypass hole. The necessity complicates the structure.

In order to solve the above-mentioned inconvenience, JP-A-61-76782 discloses that the rear side of the base wall of the fixed scroll is divided into a discharge chamber located on the center side and a low-pressure chamber located on the outer peripheral side, and the base end is formed. An annular rotary valve plate that is rotatably slidably disposed in the low-pressure chamber so as to surround the discharge chamber with respect to the rear surface of the wall, and that allows the bypass hole and the low-pressure chamber to communicate with the rotary valve plate. An apparatus is disclosed in which a hole is formed, and a rotary valve plate is rotated by a rotation adjusting mechanism to open and close a plurality of bypass holes with one rotary valve plate.

[Problems to be Solved by the Invention] However, in the variable mechanism using the bypass passage, when the rotation speed of the compressor is in the high speed region, the closed space whose volume is decreasing is instantaneously connected to the entrance of the bypass passage. As a result, the refrigerant gas is less likely to be recirculated to the suction pressure region through the bypass passage than in the case of low-speed rotation. Therefore, when used in an automotive cooling system, during high-speed operation, the variable bypass function does not work so much and cooling is excessive, so that the compressor that transmits the rotation of the engine to the drive shaft is stopped to stop the operation of the compressor, or to overcool. It cannot be prevented. Preventing overcooling by turning on and off the clutch not only eliminates the meaning of the variable capacity, but also has the disadvantage of deteriorating the driving feeling of the vehicle. If the inlet of the bypass passage is enlarged to enhance the variable effect in the high-speed region, the amount of refrigerant gas recirculated in the low-speed region becomes too large and the variable effect becomes too effective, and conversely, the variable effect in the low-speed region However, if the inlet of the bypass passage is made smaller for the purpose of aptitude, there is a problem that the variable effect in the high speed region is reduced.

The present invention has been made in view of the above problems, and an object of the present invention is to provide a variable displacement scroll compressor capable of providing an appropriate variable effect in all regions from low speed to high speed. .

Means for Solving the Problems In order to achieve the above object, according to the present invention, a fixed scroll accommodated in a housing and a movable scroll provided so as to be non-rotatable and revolvable opposed to the fixed scroll are provided. In a scroll compressor that forms a closed space whose volume decreases based on the revolution of a movable scroll, a suction throttle mechanism that can change the passage cross-sectional area on an introduction path for introducing refrigerant gas into a compression chamber is provided. A discharge chamber located at the center and a low-pressure chamber located on the outer peripheral side are defined on the rear side of the base wall of the fixed scroll, and the base wall of the fixed scroll stands on the base walls of the scrolls. A plurality of bypass holes are provided for communicating the low-pressure chamber with the volume-decreasing area of the sealed space that shifts to the center side of the provided spiral part, and the bypass hole on the back surface of the base end wall of the fixed scroll is provided. An annular rotary valve plate is rotatably provided around the discharge chamber in a position corresponding to the portion where the pass hole is formed in a state of slidingly contacting the base end wall, and the rotary valve plate includes the bypass hole and the low-pressure chamber. A communication hole which can be communicated is formed, and a rotation adjusting mechanism for rotating the rotary valve plate in relation to a load capacity is provided.

According to the second aspect of the invention, the suction throttle mechanism is provided on an introduction passage for introducing refrigerant gas into a suction chamber of the compressor, and the throttle spool and the passage of the throttle spool through the introduction passage are cut off. A biasing means for biasing in a direction to reduce the area, and a control pressure chamber to which a control pressure against the biasing means is supplied, wherein the rotation adjusting mechanism includes a pin protruding from a rotary valve plate; It comprises a cylinder accommodating a piston having a piston rod to be engaged, and a spring for urging the piston in a predetermined direction. The control valve, which operates according to the suction refrigerant gas pressure before throttling, rotates the suction throttling mechanism. The movement adjustment mechanism is interlocked.

In the invention according to the third aspect, a discharge chamber located at the center and a low-pressure chamber located at an outer peripheral side are formed on the rear side of the base wall of the fixed scroll, and the base wall of the fixed scroll has A plurality of bypass holes are provided for communicating the low-pressure chamber with the volume-decreasing area of the sealed space that shifts to the center side of the spiral portion provided upright on the base walls of both scrolls, and a plurality of bypass holes are provided on the rear surface of the base wall of the fixed scroll. An annular rotary valve plate is provided at a position corresponding to the portion where the bypass hole is formed so as to be rotatable around the discharge chamber in a state in which the annular rotary valve plate is in sliding contact with the base end wall. And a rotation adjusting mechanism for rotating the rotary valve plate in relation to the load capacity, and a suction chamber provided on the rear side of the base end wall of the fixed scroll. To proximal end wall of the scroll and the suction chamber and the compression chamber to form a through hole that communicates, the rotary valve plate to form a throttle hole that can communicate with the suction chamber and the translucent hole.

[Operation] In the present invention, the opening / closing control of the bypass hole is performed via the rotary valve plate, and the structure of the opening / closing mechanism is simplified even if the number of bypass holes is large. In the bypass opening / closing mechanism, the variable effect decreases as the rotation speed increases, but in the suction throttle mechanism, as the rotation speed increases, the passage resistance of the refrigerant gas increases and the variable effect increases. In the compressor of the present invention, the bypass opening / closing mechanism having a large variable effect in the low-speed region and the suction throttle mechanism having the large variable effect in the high-speed region mutually compensate for the variable operation in the rotational speed region where the variable effect is difficult to exert. The appropriate variable action is performed in the entire region from the low speed region to the high speed region.

According to the second aspect of the present invention, the bypass opening / closing mechanism and the suction throttle mechanism are interlockingly controlled by a control valve that operates in accordance with the suction refrigerant gas pressure before the throttle, so that the capacity control by the bypass and the capacity control by the throttle are variable. Mutual compensation of operation is ensured.

According to the third aspect of the present invention, the refrigerant gas introduced into the suction chamber is introduced into the compression chamber through a through hole formed in the base end wall. When the cooling load is large and the rotary valve plate is rotated in the direction to close the bypass hole by the rotation adjusting mechanism, the position of the throttle hole is moved so that the cross-sectional area of the through hole increases. Conversely, when the cooling load is reduced and the rotary valve plate is rotated in a direction to open the bypass hole, the position of the throttle hole is moved so that the passage cross-sectional area of the through hole becomes smaller. That is, when the rotary valve plate rotates in relation to the load capacity, the throttle control of the refrigerant gas is performed at the same time.

Embodiment 1 Hereinafter, a first embodiment of the present invention will be described with reference to FIGS.

As shown in FIG. 1, a front housing 1 and a rear housing 2 are joined and fixed, and an annular fixed substrate 3 is fitted and fixed to the inner surface of the front end of the rear housing 2 so as to be in contact with the end surface of the front housing 1. An eccentric shaft 5 projects from the large diameter portion 4a of the rotating shaft 4 housed in the front housing 1 into the rear housing 2. A balance weight 6 and a bush 7 are rotatably supported on the eccentric shaft 5, and a movable scroll 8 is rotatably supported on the bush 7 via a bearing 7a. A fixed scroll 9 is accommodated and fixed in the rear housing 2 so as to face the orbiting scroll 8, and sealed spaces (compressed spaces) C 1, C 2 are formed by base end walls 8 a, 9 a and spiral portions 8 b, 9 b of both scrolls 8, 9. Is formed.

A fixed ring 10 is fixed on the fixed substrate 3 facing the orbiting scroll 8, and a plurality of circular revolving position regulating holes 10 a are provided in the fixed ring 10 at regular intervals. The orbiting position regulating hole is provided on the back surface of the base end wall 8a of the orbiting scroll 8.
A movable ring 11 having the same number of circular revolving position regulating holes 11a opposed to 10a is fastened. Revolution position regulating holes
Disc-shaped shoes 12a, 12b having smaller diameters are accommodated in 10a, 11a, and a ball 13 is interposed between the opposed shoes 12a, 12b. The two shoes 12a, 12b and the ball 13 are press-fitted between the fixed substrate 3 and the movable scroll 8 by a compression reaction, and are apparently integrated. Then, as shown in FIG. 2, all the shoes 12a, 12b are revolved position regulating holes 10a, 11a.
With the eccentric shaft 5 revolving around the periphery of the revolving position regulating holes 10a and 11a in the same direction with the eccentric shaft 5 interposed therebetween, the orbiting scroll 8 revolves without rotating.

In the front housing 1, a suction chamber A and an introduction passage 14 for introducing refrigerant gas into the suction chamber A are formed. The identification substrate 3 and the fixing ring 10 are provided with a plurality of passages 3a (shown in FIG. 2) for communicating the suction chamber B formed between the fixed substrate 3 and the substrate wall 9a with the suction chamber A. At the center of the inner wall of the rear housing 2, a cylindrical partition wall 2 a is integrally formed in a state of contacting the rear surface of the base end wall 9 a of the fixed scroll 9.
The inside of 2a is a discharge chamber D, the outside is an annular low-pressure chamber E, and the low-pressure chamber E communicates with the suction chamber B via a passage 15 (shown in FIG. 3). At the center of the base wall 9a, a discharge port 9c communicating with a discharge chamber D provided on the rear side of the base wall 9a and being openably closed by a discharge valve 16 is provided.
Are formed.

On the back of the base wall 9a of the fixed scroll 9, the low-pressure chamber E is provided.
An annular housing groove 17 is formed so as to surround the partition wall 2a, and an annular rotary valve plate 18 is rotatably accommodated in the accommodation groove 17. As shown in FIG. 3, a plurality of bypass holes 19a to 19d for guiding the gas in the compression spaces (closed spaces) C1 and C2 to the low-pressure chamber E are provided in the base end wall 9a at positions corresponding to the housing grooves 17. C1 and C2 are formed along the spiral direction in which the compression proceeds. On the other hand, the rotary valve plate 18 has a plurality of communication holes 20a that can communicate with the low-pressure chamber E so as to correspond to the bypass holes 19a to 19d.
-20d are also formed along the spiral direction in which compression proceeds. The communication holes 20a to 20d are formed as long holes as they are located on the outer peripheral side (low pressure side), and are opened from the low pressure side as the rotary valve plate 18 reciprocates and closed from the high pressure side. It has become.

A rotation adjusting mechanism 21 for rotating the rotary valve plate 18 is provided in the low-pressure chamber E. Rotation adjustment mechanism
A cylinder 22 forming the cylinder 21 is fixed to the rear housing 2, and a rotary valve plate 18 is provided inside the cylinder 22.
A piston 25 having a rod 24 engaged at the tip with a pin 23 projecting from the rear surface of the piston is provided so as to be able to reciprocate. A base chamber 26 of the cylinder 22 defined by the piston 25 is communicated with the low-pressure chamber E by a through hole 22a formed in the cylinder 22, and a distal chamber 27 is compressed by a through hole 22b and a pipe (not shown). It is in communication with the compression chamber C2 during the stroke. A spring 28 for urging the rotary valve plate 18 in the projecting direction of the rod 24, i.e., in the direction of opening the bypass hole, is provided in the chamber 22.
Is interposed. Spring constant and piston of the spring 28
When the suction pressure is equal to or lower than the lower limit set value, the rod 24 is disposed at the projecting position and all the bypass holes 19a to 19d are opened, and when the suction pressure is equal to or higher than the upper limit set value, the rod 24 is closed.
Are arranged at the retracted position, all the bypass holes 19a to 19d are closed, and when the suction pressure is between the two set values, each is set so that the protrusion amount of the rod 24 can be changed according to the suction pressure. I have. The rotation adjusting mechanism 21 and the variable bypass mechanism are the same as those disclosed in JP-A-61-76782.

The introduction passage 14 extends in parallel with the rotary shaft 4 so that one end thereof opens to the front end side of the front housing 1 and also serves as a housing for accommodating the throttle spool 29; Communication part 14b communicating with A
And is formed from A throttle spool 29 is provided in the storage section.
Are arranged so as to be slidable in a direction orthogonal to the communication portion 14b and in a state where the control pressure chamber S is defined and formed in the housing portion by the throttle spool 29. The throttle spool 29 is formed in a hollow shape with the control pressure chamber S side closed, and a plurality of openings 30 having the same length as the diameter of the communication portion 14b are formed near the closed end thereof. The throttle spool 29 is urged by a pressing spring 31 as urging means interposed in the hollow portion in a direction in which the cross sectional area of the introduction passage 14 is reduced, that is, in a direction in which the volume of the control pressure chamber S is reduced. The throttle spool 29, the pressing spring 31, and the control pressure chamber S constitute a suction throttle mechanism.

In the control valve mechanism 32 for controlling the suction throttle mechanism, a diaphragm 34 is incorporated in a valve housing 33, and a ball valve 35 is connected to the diaphragm 34 via a rod 35a. The input port 33a on the peripheral surface of the valve housing 33 is connected to the suction pressure region of the rear housing 2 via a pipe 36a, and the input port 33b on the lower surface is connected to the discharge chamber D via a pipe 36b. An output port 33c on the peripheral surface of the valve housing 33 is connected to the control pressure chamber S via a conduit 36c. The pressure chamber 33d defined in the valve housing 33 by the diaphragm 34 is connected to the introduction portion 14 through a conduit 36d.
It is connected to the inlet side of the throttle spool 29 of a.

Next, the operation of the compressor configured as described above will be described.

Scroll 8b of movable scroll 8 with rotation of rotating shaft 4
Is revolved clockwise in FIG. 3 while locally contacting the spiral portion 9b of the fixed scroll 9, the contact portion between the two spiral portions 8b, 9b moves toward the center on the inner peripheral surface of the spiral portion 9b. The compressed spaces C1 and C2 formed between the two contact portions move and the introduction passages 14 are formed.
Compressed refrigerant gas is gradually moved to the center side while compressing the refrigerant gas introduced into the compressor, and the compressed refrigerant gas is discharged into the discharge chamber D from the discharge port 9 c which is openably closed by the discharge valve 16. .

When the cooling load is large, that is, the pressure chamber of the control valve mechanism 32
When the suction pressure introduced into 33d is high, the diaphragm 34 is pushed up from the state shown in FIG. 1, and the ball valve 35 closes one input port 33a and opens the other input port 33b. As a result, the refrigerant gas discharged from the discharge chamber D is supplied to the control pressure chamber S, and the pressure in the control pressure chamber S rises to a pressure corresponding to the discharge pressure. When the control pressure chamber S becomes high pressure equivalent to the discharge pressure, the throttle spool 29 moves against the pressing spring 31, and the communication portion 14b of the introduction passage 14 and the opening 30 of the throttle spool 29 completely correspond to each other. . In this state, the passage cross-sectional area in the introduction passage 14 is maximized, and operation with a large capacity is possible.

When the cooling load is large, the gas pressure introduced into the chamber 27 of the cylinder 22 of the rotation adjusting mechanism 21 moves the piston 25 toward the retracting side of the rod 24 against the urging force of the spring 28. As a result, the rotary valve plate 18
Each of the bypass holes 19a-1
9d is closed in order to prevent the refrigerant gas in the compression spaces C1 and C2 from flowing out to the low-pressure chamber E through the bypass hole. As a result, the compressor is in a 100% operating state.

On the other hand, when the cooling load is small, that is, when the suction pressure is low, the diaphragm 34 is pushed down and the ball valve 35 closes the input port 33b side and opens the input port 33a. As a result, a portion corresponding to the suction pressure in the rear housing 2 communicates with the control pressure chamber S, and the pressure in the control pressure chamber S decreases to a pressure corresponding to the suction pressure. When the control pressure chamber S has a low pressure equivalent to the suction pressure, the opening 30 of the throttle spool 29 shifts from the position corresponding to the communication portion 14b, and the passage cross-sectional area in the introduction passage 14 is reduced. Further, the gas pressure introduced into the chamber 27 of the cylinder 22 of the rotation adjusting mechanism 21 becomes smaller than the urging force of the spring 28, and the piston 25
Is moved to the projecting side of the rod 24. Thereby, the rotary valve plate 18 is rotated in a direction to open the respective bypass holes 19a to 19d, the respective bypass holes 19a to 19d are sequentially opened, and the refrigerant gas in the compression spaces C1 and C2 passes through the bypass holes 19a to 19d and It flows out to the low-pressure chamber E through the communication holes 20a to 20d. This reduces the compression capacity. When the suction pressure falls below the lower limit set value, all the bypass holes 19a to 19d are kept open.

That is, when the cooling load is small, the variable functions of the suction throttle mechanism and the bypass opening / closing mechanism act. The bypass opening / closing mechanism reduces the variable effect as the rotation speed of the rotating shaft 4 increases, and the refrigerant gas passes as the rotation speed increases. When used in combination with a suction throttle mechanism that increases the resistance and increases the variable effect, the variable effects in the rotational speed range where each variable effect is difficult to exert are mutually compensated, and are appropriate over the entire range from the low speed range to the high speed range Variable action is performed. Therefore, when the compressor is used for an automobile cooling system, it becomes too cool at the time of high-speed operation, and there is no need to stop the operation of the compressor by disengaging the clutch that transmits the rotation of the engine to the rotating shaft 4 and disengaging the clutch. As a result, the inconvenience that the driving feeling of the vehicle deteriorates due to the impact caused by the shock is surely avoided.

Second Embodiment Next, a second embodiment will be described with reference to FIG. This embodiment differs from the previous embodiment in that both the suction throttle mechanism and the rotation adjusting mechanism 21 are controlled by a control valve mechanism 32. In this embodiment, contrary to the previous embodiment, the rod 24 moves in the protruding direction so that the rotary valve plate is moved.
18 is rotated in the direction of closing the bypass hole. The proximal chamber 26 provided in the cylinder 22 is a pipe 36e.
Is connected to the output port 33e of the valve housing 33, and the chamber 27 on the distal end side is communicated with the low-pressure chamber E through a through hole 22b. A spring 28 that urges the rod 24 in the retracting direction, that is, the rotary valve plate 18 in the direction of opening the bypass hole, is interposed in the chamber 27.

Therefore, in this embodiment, when the cooling load is large, the throttle spool 29 is arranged at a position where the passage cross-sectional area in the introduction passage 14 is maximized by the operation of the control valve mechanism 32 as described above. At this time, the discharge pressure is supplied to the chamber 26 of the cylinder 22 via the pipe 36e, and the piston 25 is moved to the projecting side of the rod 24 against the urging force of the spring 28. As a result, the rotary valve plate 18 is rotated in a direction to close the bypass holes 19a to 19d, and the respective bypass holes 19a to 19d are closed.
As a result, the compressor is in a 100% operating state. On the other hand, when the cooling load is small, the control valve mechanism 32
The throttle spool 29 is moved by the action of
The passing cross-sectional area at is reduced. In addition, the rotation adjustment mechanism 21
The gas corresponding to the suction pressure is supplied to the chamber 26 of the cylinder 22.
The piston 25 is moved toward the retracted side of the rod 24 by the force of the spring 28. This allows the rotary valve plate 18
Is rotated in a direction to open the bypass holes 19a to 19d, and the bypass holes 19a to 19d are opened to reduce the compression capacity.

That is, in this embodiment, the adjustment of the throttle of the suction throttle mechanism and the opening and closing of the bypass opening / closing mechanism are reliably interlocked by the supply of either the discharge pressure or the suction pressure by the control valve mechanism 32.

Third Embodiment Next, a third embodiment will be described with reference to FIGS. In this embodiment, the suction throttle mechanism is a rotary valve plate.
18 differs greatly from the above-mentioned embodiments in that it is incorporated in 18. As shown in FIG. 5, a suction hole 37 for refrigerant gas is formed in the rear housing 2 at a position corresponding to the low-pressure chamber E on the rear surface of the base end wall of the fixed scroll 9, and a part of the low-pressure chamber E is connected to the suction chamber A. Has become. A through hole 38 is formed in the base end wall 9a to allow the suction chamber A to communicate with the compression chamber via the suction chamber B.
The outer diameter of the rotary valve plate 18 is substantially the same as that of the base end wall 9a, and a throttle hole 39 is formed to allow the through hole 38 to communicate with the suction chamber A. When the rotary valve plate 18 is rotatably arranged at a position where each of the bypass holes 19a to 19c is opened, the throttle hole 39 has a position where the cross-sectional area of the through hole 38 is minimized, and the throttle hole 39 closes each of the bypass holes 19a to 19c. Is formed at a position where the cross-sectional area of the through hole 38 is maximized when it is rotated.

Therefore, in the compressor of this embodiment, when the cooling load is large, when the rotary valve plate 18 is rotated in the direction of closing the bypass holes 19a to 19c by the operation of the rotation adjusting mechanism 21, the passage of the passage hole 38 is cut off. The area is maximized, and the compressor is in the maximum capacity operation state. On the other hand, when the cooling load is small, when the rotary valve plate 18 is rotated in the direction of opening the bypass holes 19a to 19c by the action of the rotation adjusting mechanism 21, the passage cross-sectional area of the through hole 38 is minimized, The compressor is in a small capacity operation state. That is, in this embodiment, the suction throttle mechanism is provided with the through hole 38 formed in the base end wall 9a of the fixed scroll 9.
And a throttle hole 39 formed in the rotary valve plate 18, and the suction throttle is controlled by the rotation adjusting mechanism 21 of the rotary valve plate 18, so that the mechanism is simplified.

The present invention is not limited to the above-described embodiment. For example, in the first and third embodiments, the drive of the rotary valve plate 18 may be configured to be performed by a step motor,
An intermediate pressure in the compression space C1 may be applied to the chamber 26 on the proximal end side of the cylinder 22 and an intermediate pressure or a discharge pressure higher than the intermediate pressure may be applied to the chamber 27 on the distal end side. Alternatively, the differential pressure between the suction pressure and the set pressure may be electrically measured, and the suction pressure and the intermediate pressure may be selected by an electromagnetic valve that operates based on the difference. Further, the number and position of the bypass holes may be arbitrarily changed.

[Effects of the Invention] As described above in detail, according to the present invention, the opening and closing control of the bypass hole is performed via the rotary valve plate, and the structure of the opening and closing mechanism is simplified even when the number of bypass holes is large. You. In addition, the bypass opening / closing mechanism having a large variable effect in the low-speed region and the suction throttle mechanism having a large variable effect in the high-speed region mutually compensate for the variable operation in the rotational speed region where the variable effect is difficult to be exhibited. The appropriate variable action is performed in the entire range from to the high speed range. Therefore, when used in an automotive cooling system, the operation of stopping the compressor by disengaging the clutch that transmits the rotation of the engine to the rotating shaft due to excessive cooling during high-speed operation becomes unnecessary, so that the clutch can be turned on and off. The inconvenience that the driving feeling of the automobile is deteriorated by the accompanying impact is reliably avoided.

According to the second aspect of the present invention, in addition to the above-described effects, the bypass opening / closing mechanism and the suction throttle mechanism are interlocked and controlled by a control valve that operates in accordance with the suction refrigerant gas pressure before the throttle. The mutual compensation of the variable action with the capacity control by the control is surely performed.

According to the third aspect of the present invention, in addition to the above-described effects, the suction throttle mechanism is incorporated in the rotary valve plate, and the rotation of the rotary valve plate is also interlocked to control the suction throttle, thereby simplifying the mechanism. .

[Brief description of the drawings]

1 to 3 show a first embodiment of the present invention. FIG. 1 is a sectional view taken along line II of FIG. 3, and FIG. 2 is a line II-II of FIG. FIG. 3 is a sectional view taken along the line III-III of FIG. 1, FIG. 4 is a sectional view of the second embodiment, and FIGS.
FIG. 5 is a sectional view showing an embodiment, and FIG. 6 is a partially omitted sectional view taken along line VI-VI of FIG. Front housing 1, rear housing 2, movable scroll 8, fixed scroll 9, base end walls 8a, 9a, spiral parts 8b, 9
b, introduction passage 14, introduction part 14a, communication part 14b, rotary valve plate 18, bypass holes 19a to 19d, communication holes 20a to 20d,
The rotation adjusting mechanism 21, the cylinder 22, the pin 23, the rod 24, the piston 25, the throttle spool 30 constituting the suction throttle mechanism, the pressing spring 31 as the urging means, the control pressure chamber S, and the control valve mechanism 3
2. Suction hole 37, through-hole 38 forming a throttle mechanism, throttle hole 39, suction chambers A and B, compression spaces (closed spaces) C1 and C2, discharge chamber D, low-pressure chamber E, and control pressure chamber S.

──────────────────────────────────────────────────続 き Continued on the front page (58) Field surveyed (Int.Cl. ⁶ , DB name) F04C 18/02 311 F04C 29/10 311

Claims (3)

(57) [Claims] An enclosed space, whose volume is reduced based on the revolution of a movable scroll, between a fixed scroll accommodated in a housing and a movable scroll provided so as to be non-rotatable and revolvable facing the fixed scroll. In the scroll compressor to be formed, a suction throttle mechanism capable of changing a passage cross-sectional area thereof is provided on an introduction path for introducing a refrigerant gas into a compression chamber, and a suction throttle mechanism is provided at a central portion on the back side of a base end wall of the fixed scroll. And a low-pressure chamber located on the outer peripheral side, and the volume of an enclosed space that moves to the center side of the spiral portion provided on the base end walls of the two scrolls on the base end wall of the fixed scroll is reduced. A plurality of bypass holes for communicating a developing region with the low-pressure chamber, and an annular rotary valve at a position corresponding to a portion where the bypass hole is formed on the back surface of the base end wall of the fixed scroll; A rate is provided so as to be rotatable around the discharge chamber in a state of sliding contact with the base end wall, a communication hole is formed in the rotary valve plate so as to allow communication between the bypass hole and the low-pressure chamber, and a load is applied to the rotary valve plate. A variable displacement scroll compressor provided with a rotation adjusting mechanism for rotating in relation to the displacement. 2. The suction throttle mechanism is provided on an introduction passage for introducing refrigerant gas into a suction chamber of a compressor, and reduces a throttle spool and a cross-sectional area of the introduction passage through the throttle spool. And a control pressure chamber to which a control pressure opposing the biasing means is supplied, wherein the rotation adjusting mechanism engages a pin protruding from a rotary valve plate. The suction throttle mechanism and the rotation adjustment mechanism are constituted by a cylinder in which a piston having a rod is accommodated, and a spring that biases the piston in a predetermined direction, and are controlled by a control valve that operates according to the suction refrigerant gas pressure before throttling. The variable capacity scroll type compressor according to claim 1, wherein the variable capacity scroll type compressor is controlled in conjunction with the scroll. 3. A closed space, whose volume is reduced based on the revolution of the movable scroll, between a fixed scroll accommodated in the housing and a movable scroll provided so as not to rotate and revolve in opposition to the fixed scroll. In the scroll-type compressor to be formed, a discharge chamber located at a central portion and a low-pressure chamber located at an outer peripheral side are formed on a rear side of a base end wall of the fixed scroll, and the two scrolls are formed on a base end wall of the fixed scroll. A plurality of bypass holes communicating between the low-pressure chamber and the volume-decreasing region of the closed space which shifts to the center side of the spiral part erected on the base wall of the fixed scroll, and the bypass hole on the back surface of the base wall of the fixed scroll An annular rotary valve plate is provided rotatably around the discharge chamber in a position corresponding to the portion where the is formed, in a state of slidingly contacting the base end wall. A bypass hole and a low pressure chamber to form a communication hole which can communicate, and provided a rotation adjustment mechanism for rotating with respect to the rotary valve plate to the load capacity,
And, the suction chamber is provided on the rear side of the base end wall of the fixed scroll, and a through hole is formed in the base end wall of the fixed scroll to allow the suction chamber and the compression chamber to communicate with each other. A variable displacement scroll compressor with a throttle hole that can communicate.