JPS5982597A - Capacity varying type compressor - Google Patents

Abstract

PURPOSE:To prevent malfunction of a control valve, by a method wherein a spool is openably/closably located in a bypass hole for communicating a compression chamber with a suction chamber, the pressure detector of the spool is forced into coincidence with the phase of both compression blocks, and a low pressure side detecting part is situated so as to front on the compression chamber in the primary stage of compression. CONSTITUTION:In a control valve mechanism 12, a spool 19 for opening/closing a bypass hole 11 is slidably situated opposite to the bypass hole 11. From a high pressure chamber 20 at the end of the spool 19, a first pressure induction hole 23 extends and the forward end thereof is located so as to be rendered effective during compression stroke of a compression chamber 6. A second pressure guide hole 24 extends from a low pressure chamber 21, and the forward end thereof is situated so as to be rendered effective during the suction stroke of the compression chamber 6. Further, pressure detecting parts 23' and 24' have a phase angle of 90 deg. shifted from each other, and this permits prevention of malfunction of a control valve.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a variable compression capacity compressor that can automatically control compression capacity in accordance with changes in indoor cooling load. More specifically, the suction stroke pressure P
A control valve is provided so as to be able to be automatically opened and closed by utilizing a change in the differential pressure that occurs between L (pressure during the suction stroke in the suction chamber or compression chamber) and compression stroke pressure PH (pressure during the compression stroke in the compression chamber), By automatically opening and closing the control valve, part of the refrigerant gas that is being compressed in the compression chamber is released to the suction chamber during low cooling loads, thereby automatically adjusting the compression capacity in the compression chamber. This invention relates to improving the control valve mechanism of a variable capacity compressor installed in a compressor, and improving its control function, more specifically, suppressing the range of variation in differential pressure that occurs between suction stroke pressure PL and compression stroke pressure PH. The purpose of this is to prevent malfunction of the control valve.

Conventionally, variable capacity compressors have been designed to fully automatically control the compression capacity in response to changes in the cooling load in the room. (ii) The method used, more specifically, when comparing the change in differential pressure that occurs between the pressure in the suction chamber and the pressure in the compression chamber during the compression stroke, the difference is proportional to the degree of pressure in the suction stroke. In view of the large pressure change, the control valve mechanism is automatically opened and closed by making full use of this differential pressure change, and a part of the refrigerant gas in the middle of compression is released into the suction chamber, thereby increasing the compression capacity. A method of adjustment has previously been proposed (for example, JP-A-57-122191). However, in the above proposal, the difference between the suction stroke pressure PL (pressure inside the suction chamber) and the compression stroke pressure PH is The problem is that if the pressure fluctuates widely and damping due to throttling or the like is insufficient, malfunctions are likely to occur when opening and closing the spool.

In other words, as shown in Fig. 9, the suction stroke pressure PL (pressure inside the suction chamber) hardly changes for one revolution of the rotating shaft, whereas the compression stroke pressure PH + C changes as the rotation angle of the rotating shaft changes. It fluctuates greatly. More specifically, for example, in a slide vane type compressor, four vanes 7 are provided in a compression chamber so as to be freely retractable, and the inside of the compression chamber is divided into four compression blocks by the vanes, and each compression block is
When continuously moving from the suction side to the discharge side,
Compression stroke pressure P at which a particular vane is provided during the compression stroke
Immediately after passing the pressure detection part of H, the detected pressure is at its lowest state, and as the succeeding vane approaches the same pressure detection part, the detection pressure gradually increases until the same vane passes all the way through the pressure detection part. The highest pressure state is detected just before the vane passes through the pressure detection part, the pressure drops rapidly, and the lowest pressure state is detected again. It is repeated four times.

As the detected pressure at the compression stroke pressure pH fluctuates greatly in this way, the differential pressure ΔP generated between the compression stroke pressure pH and the suction stroke pressure PL also becomes ΔPm! □.

ΔPma and x will fluctuate significantly, and this drastic variation in differential pressure will cause the spool to malfunction, causing the spool to open during heavy cooling loads and reduce the compression capacity. Otherwise, problems may occur such as the spool closing and the compression capacity increasing during a small cooling load.

The present invention is an attempt to improve the conventional situation in view of the above-mentioned conventional situation, and a pressure detection part for the suction stroke pressure PL is provided in the compression chamber during the suction stroke (at a position including the initial stage of the compression action). , the detected pressure of the suction stroke pressure PL is the compression stroke pressure P
The feature is that by changing the pressure in synchronization with the detected pressure of rain H, it is possible to suppress the fluctuation range of the differential pressure that occurs between the rain detected pressures as small as possible.

The gist of the present invention is to provide a compressor in which a compression chamber is divided into a plurality of compression blocks, and each compression block is provided so as to be able to move continuously from the suction side to the discharge side. A spool is provided so that it can be opened and closed with respect to the bypass hole that communicates with it, and the spool is normally biased in the opening direction, and a pair of pressure chambers are provided facing each other at both ends of the spool. The pressure detecting sections of both pressure chambers are arranged so that each pressure detecting section can face another compression block, and both positive force detecting sections are aligned in phase with respect to the surface compression block, and the pressure detecting sections are arranged so that each pressure detecting section can face another compression block. The reason is that the pressure detection section on the side is configured to face the compression chamber in the initial stage of compression action.

DESCRIPTION OF THE PREFERRED EMBODIMENTS The drawings illustrating all specific embodiments of the present invention will be described below.

1 to 5 are drawings showing a first embodiment, and in each drawing, (1) indicates a housing forming the outer shell of the compressor. The same housing (llif) is formed by the front housing (IA) and the rear housing (IB), and the front housing (IA) has a half linder block (2), which is also sandwiched between the lif linder block (2). A front sight grate (3A) and a catcher side plate (3B) are fitted on both sides./The linder block (2) is formed into a hollow cylindrical shape with openings at both front and rear ends, and the inside of the hollow part The wall is / Linder block (2
) is formed in a cylindrical shape concentric with the outer peripheral surface of the Norinder Bronnok (2).Both the front and rear openings of the Norinder Bronnok (2) are shielded by the above-mentioned both side plates (3A) (3B). There is a drive shaft (4) between 3A) and (3B).
is suspended horizontally. The drive shaft (4) is connected to the cylinder block (
The rotor (5) is integrally fixed to the drive shaft (4).

The rotor (5) is provided so that a part of its outer peripheral wall can slide against the inner wall surface of the cylinder block (2),
The outer peripheral wall of the rotor (5) and the cylinder block (2)
A compression chamber (6) is formed between the inner wall surfaces of.

Furthermore, four vanes (8) are fitted into the rotor (5) so as to be retractable into the compression chamber (6). And each base
7 (8)... is a compression chamber (6) made up of four compression blocks (
6a) (6b) (6c) (6d),
While each compression block (6a) (6b) (6c) (6d) is continuously moved from the suction side to the discharge side, the compression chamber (6)
It is installed so that it rotates inside.

A suction chamber (9) is provided between the front housing (IA) and the front side grate (3A).
) is provided with a suction port (9)' connected to a suction pipe (not shown) on the front bousing (IA) side. Further, a suction hole (10) is opened in the front side dale 1-(3A) corresponding to one end of the compression chamber (6), that is, the starting end along the rotational direction of the rotor (5). Furthermore, a bypass hole (]l) is provided through the front side plate (3A), located approximately midway between the suction stroke and the compression stroke (at the beginning of the compression stroke) of the compression chamber (6). The bypass hole (11) is provided so as to communicate between the compression chamber (6) and the suction chamber (9).
There is a control valve mechanism (1) in the front side brake (3A).
21 is provided in the direction perpendicular to the bypass hole (marked). (The control valve mechanism (12) will be described later.) On the other hand, the other end of the compression chamber (6), that is, along the rotation direction of the rotor (5) A part of the cylinder block (2) is cut out at a position corresponding to the terminal end.
A discharge chamber 03) is formed between the inner wall surface of A) and the inner wall surface of 71. The discharge chamber (13) and the terminal end of the compression chamber (6) are communicated with each other through a discharge hole. (15) is the same discharge hole Q4) k N
There is a rear sight plate (3) in the rear housing (IB).
A lubricating oil separation chamber 07) is formed between the lubricating oil and B).

The separation chamber 071 is provided so as to communicate with the discharge chamber (12) through a through hole (18) e opened in the barrier side plate (3B). A filter (not shown) is provided at the opening of the through hole 08), and a lubricating oil reservoir separated by the filter is provided in the separation chamber (I7). The same separation chamber 07) also has a discharge port θ connected to a discharge pipe (not shown) on the rear housing (IB) side.
7)' is provided.

A spool 09) for opening and closing the bypass hole (11) is provided in the control valve mechanism (12) in correspondence with the bypass hole (old) so as to be slidable in a direction perpendicular to the bypass hole (old). A pair of pressure chambers consisting of a high pressure chamber (20) and a low pressure chamber (21) are provided facing each other at both ends of the spool 09). There is a splash (22j) inside the low pressure chamber (21).
is installed, and the spool 09) is normally biased toward the high pressure chamber (20) via the spring (22)', so that the bypass hole Cl1) is fully opened. A first pressure guiding hole (23) is extended from the high pressure chamber (20), and its tip (pressure detection part (231') ) from which a second pressure guiding hole (24) extends, and its tip (pressure detection part (24)
41"J is a surface pressure detection part (2
3)'(24)i are provided with a phase angle of 90 degrees from each other (ie, the same as the phase angle between each vane (8)...). In other words, the surface pressure detectors (23)'(2(a)' are provided so that they do not face the same compression block at the same time, but instead face each of the adjacent compression blocks in the middle of compression. .And the same pressure detection part (23)'
(24) 'c) In other words, a single-force pressure detection unit is installed so that it faces the compression block with the same phase angle (231' can face the inside of a specific compression block). At the same time, the other pressure detecting section (24)' is also provided so as to face into the adjacent compression block.

6 and 7 are drawings showing the second embodiment, and in both drawings (31) indicates a housing forming the outer shell of the compressor. The nousing (31) is composed of the front housing (3) and the Liano Ujifugu (33), and the front nozzle 1 (32) is the front wall part (32a).
) and a peripheral wall (32b) surrounding the outer periphery of the front wall (32a), which is formed into a cylindrical shape with a bottom. , a peripheral wall portion (33b) surrounding the outer periphery of the rear wall portion (33a).
It is formed into a cylindrical shape with a bottom.

The interior of the front housing 02) is divided into two rooms via a partition plate (341') fitted approximately in the middle thereof.

That is, a suction chamber (35) is provided on the front wall (32a) side, and a compression chamber (36) is provided on the opening side. The suction chamber (35) and the compression chamber (36) are provided to communicate with each other through a through hole (34)' opened in the partition panel (34), and the compression chamber (36) is provided with a fixed scroll ( 37) and a rotating scroll (38), which will be described later. The fixed scroll C37) has a base (C37) that fits into the inner wall surface of the front housing (32) along the opening edge thereof.
37a) and a scroll piece (37b) that protrudes spirally from the base (37a) toward the front housing (three front walls (32a).The suction chamber (35) has a peripheral wall part. (32b) is a suction pipe (not shown)
The inlet (=IO) connected to the front wall part (32
A) is provided with a bearing section (41). A drive shaft (42) is rotatably supported in bearing section 6+11. One end of the drive shaft (42) on the same side that protrudes outside the front nozzle (32) is connected to an electromagnetic clutch (not shown). On the other hand, a crankshaft (42)' is provided at the other end extending into the front housing (321) so as to face the compression chamber (36), and the crankshaft (G42)' is provided with the aforementioned rotating scroll (42)'. 38) is mounted on an axis so as to be swingable and rotatable.

The rotating scroll roll C38) is formed by a base (38a) and a scroll piece (38b) that protrudes from the base (38a) in an i-wound shape toward the fixed scroll (41'). 38b) ID fixed scroll (3η scroll piece (37b) is provided with its winding direction different from that of the scroll piece (37b)).

The same scroll piece (38b) is provided so as to be able to slide against the base (37a) on the H fixed scroll (37) side, while the fixed scroll C is attached to the base (38a).
The scroll piece (37b) on the side 37) is provided so as to be able to come into sliding contact with each other, and six compression chambers are formed in a spiral shape between both the scroll pieces (37b) and (38b). The compression chamber (a) is formed by a plurality of compression blocks (55a) (55b) through the sliding action of both scroll pieces (37b) (38b).
) (55cH55dH55e) Each compression block is provided so as to be able to move continuously from the suction side to the discharge side.

On the other hand, as mentioned above, by fitting the base (37a) of the fixed scroll (3γ) into the opening of the front nozzle (33), the base (37a) is attached to the rear nozzle (33) side.
A suction chamber (39') is formed between the compression chamber (36) and the compression chamber (36) via the discharge chamber (431) and the through hole (3.1)'.

The discharge chamber (431, K has a discharge pipe line (
A discharge hole (441) is provided in the base (37a), which is connected to a discharge hole (441, not shown), which corresponds to the center of the spiral formed by the scroll piece (37b).
5) is opened, and the discharge hole (45) has a discharge valve (45).
' is provided so that it can be opened and closed freely. (4G) indicates a glue retainer for regulating the opening angle of the discharge valve (4').

Also, the fixed scroll (3-force base (37a) has the above-mentioned suction chamber (, 35)' and compression chamber (4) (closer to the suction stroke).
A bypass hole (39) is provided so as to communicate therebetween, and a control valve mechanism t=17+ for the bypass hole (39) is provided in the bypass hole (39). A spool (48) is provided in the control valve mechanism (47) so as to be slidable in a direction perpendicular to the bypass hole (39). A high pressure chamber 6191 and a low pressure chamber (50
) A pair of pressure chambers are provided facing each other. A spring ◎1) is installed in the low pressure chamber (50), and the spool (18
1i and the same spring (51) always create a high pressure chamber (=19)
The bypass hole (39) is provided so as to be biased toward the direction to open the bypass hole (39). and hyperbaric chamber (49)
The first pressure guiding hole TBS extends from the first pressure guiding hole TBS, and its tip (pressure detecting part 6') receives the second guiding pressure from the low pressure chamber (50) during the compression stroke of the compression chamber (toward). A hole (2) is extended, and its tip (pressure detection part (a)') faces each of the compression chambers (positions during the five suction strokes (including the initial stage of compression action)). →'Q' are provided by arranging them in a line on a straight line extending radially from the center.In other words, the six pressure detecting parts 'Q' face the same compression block at the same time. Rather, they are provided so that during compression, they can face the radially adjacent compression blocks (55a) and (55c) through sliding contact between both scroll pieces (37b) and (38b), respectively. Incidentally, in cases where the scroll pieces (37b) (38b) have a large number of spiral windings, they may be placed on one compression block, respectively.

Next, its effect will be explained.

In the first embodiment shown in FIGS. 1 to 5, the driving force of the engine is transmitted to the drive shaft (4) through the connection operation of an electromagnetic clutch (not shown), and the driving force is transmitted to the rotor (4) through the driving force. 5) ff: By rotating, the same rotor (5
) and D vane (8)... through the rotational action of the compression chamber (
6) The refrigerant gas sent into the compression chamber (6) is pumped toward the discharge side. A part of the refrigerant gas that is pumped through the compression chamber (6) in this way is bypassed.
Since it is in an open state, it flows out to the suction chamber (9) side through the bypass hole (II) during compression.

In addition, the refrigerant gas sent through the compression chamber (6) to its terminal position passes through the discharge hole (141, discharge chamber (13), through hole (18), and separation chamber (17), and then from the discharge port 07)' to the discharge pipe. It is sent out along the road toward a condenser (not shown).

By repeating the above action, the compression pressure in the compression chamber (6) is gradually increased, while the pressure change in the compression chamber (6) is controlled by the pressure detection part (23+' (24).
)' is detected. And the same pressure detection part (23+
'(241') Either the differential pressure generated between the side pressures (compression stroke pressure PH and suction stroke pressure PL) detected at spool 09) exceeds the set pressure of the spring (22) in the control valve mechanism (12). By overcoming the biasing pressure of the spring (22) and being pressed in the low pressure chamber (2υ direction), a state is obtained in which the bypass hole (marked) is blocked.And by blocking the bypass hole (marked) by the spool (19) in this way, A part of the refrigerant gas in the compression chamber (6) does not flow out to the suction chamber (9) side through the bypass hole fll+'i as before, but all of it is compressed and a 100% operating state is obtained.

On the other hand, as the cooling load in the room decreases and the pressure in the suction chamber (9) decreases, the differential pressure between the suction stroke pressure PL and the compression stroke pressure pH also decreases. And that differential pressure is the spring (2
In the state where the pressure is lower than the set pressure in step 2), the pressure is pushed toward the low pressure chamber (21) by the differential pressure, and the bypass hole (l
lla - Spool in the blocked state 09) Spring + 22
)' toward the high pressure chamber (20), and a state is obtained in which the bypass mechanism (20) is opened. That is, the compression chamber (
In 6), a part of the refrigerant gas in the middle of compression enters the suction chamber (
By flowing out to the side 9), the compression pressure in the compression chamber (6) decreases, resulting in an effect of reducing the compression capacity.

According to K, the same pressure detecting section (field 2'(24)') is arranged with a phase angle of 90 degrees to match the phase angle of each vane (8)... Pressure detection part (23)
' At ', the vane (8
) approaches the pressure detection part (23)', the detected pressure reaches its maximum just before the vane (8) passes the pressure detection part (23)', and at the same time the vane (8) passes the pressure detection part (23)'. Immediately after passing through, the pressure drops rapidly and reaches its lowest value (pH in Figure 8). Also, as the succeeding vane (8) approaches, the re-O pressure is gradually increased in the rotor (5).
After that, the pressure detection part C is continuously repeated for each rotation.
24J', the same pattern as above is repeated in synchronization with the above pattern (PL in FIG. 8).

In this way, the above-described pressure fluctuation pattern is repeated synchronously in the same pressure detection section +231'(2,I)', thereby making it possible to reduce the range of fluctuation in the differential pressure that occurs between the two. That is, the fluctuation range of the differential pressure (ΔPm1n → ΔPma
x ) can be made small, which makes the spool 0
9) It is possible to stabilize the movement.

In the second embodiment shown in FIGS. 6 and 7, the driving force of the engine is transmitted to the drive shaft (42) through the connection operation of an electromagnetic clutch (not shown) provided at one end of the drive shaft (mouth). By doing so, the crankshaft portion of the drive shaft (42) (
A state is obtained in which the rotary scroll (38) mounted on the shaft 12+' oscillates (revolutions) in a state where its rotation is completely restricted. That is, the rotating scroll (: (8) scroll piece (
38b) is fixed scroll (371 side scroll piece (
37b), while swinging and rotating toward the center of the spiral. In this way, the rotating scroll (38) swings and rotates while its scroll piece (38b) is in sliding contact with the scroll piece (37b) on the fixed scroll (37) side, thereby compressing a plurality of compression chambers. Block (55a) (55b) (55c) (55dH55
e), it is possible to obtain the effect of compressing the refrigerant gas while continuously moving each compression block toward the center. Of the refrigerant gas that is continuously transferred toward the discharge side of each compression block and pumped toward the center, part of it passes through the bypass hole (39) and the suction chamber (35)' during compression. It flows out to the side. And also both scrolls (3
7) The refrigerant gas pressure-fed to the center position of (38) pushes open the discharge valve (45)' through its compression pressure, and the discharge chamber (
43).

As this action is repeated continuously, the pressure within the compression chamber is gradually increased.

Then, when the pressure detected in both pressure detection parts U'(52') (the differential pressure generated between the suction stroke pressure PL and the compression stroke pressure PH1 exceeds the set pressure of the spring 9), the control valve mechanism 48) overcomes the biasing pressure of the spring (5I) and is suppressed in the direction of the low pressure chamber (50), resulting in a state in which the hole (39) is closed.This results in a 100% operating state. is obtained.

On the other hand, as the cooling load in the room decreases and the pressure in the suction chamber (35!) decreases, the compression stroke pressure PH and suction stroke pressure PL also decrease relatively. As the pressure decreases, the differential pressure or spring (51)
In the state where the pressure is lower than the set pressure of
The spool (=1811 is the spring (5)
) in the direction of the high pressure chamber (49) to open the bypass holes (three). This has the effect of reducing compression capacity.

However, both pressure detection parts c are provided facing the compression chamber mark.
The key point is that as each compression block continuously moves through the rotation of the rotating scroll (38), pressure fluctuations are repeated each time.
2'6"i' is provided so as to face into the compressed block adjacent in the radial direction, and both detectors 62'E and (l' are provided so that their phases match with respect to the same compressed block. As a result, pressure fluctuation patterns can be obtained in synchronization in both pressure detection sections Gψ'63'.By being able to obtain pressure variation patterns in synchronization in this way, the detected pressure ( The fluctuation range of the differential pressure generated between the compression stroke pressure (Po) and the detection pressure (suction stroke pressure Pt) at the detection unit 6' can be offset, and the movement of the spool (48) as in the first embodiment can be canceled out. can be stabilized.

In addition, as described in Section 2, pressure fluctuations that occur as the rotation angle of the rotor (5) or the rotating scroll (38) changes can be handled by controlling the first and second pressure holes in the control valve mechanism. It is possible to temporarily solve this problem by making the diameter as small as possible and giving a constricting effect to the round part. However, while this method relies on the squeezing effect of the lever, it works effectively when rotating at high speeds, but the problem is that it cannot be expected to produce the squeezing effect when rotating at low speeds or when the structure does not allow for the squeezing effect. has. In contrast, in the present invention, the rotor (5) or the rotating scroll piece 38)
It is possible to obtain the effect of stabilizing the movement of the spool regardless of the rotational speed of the spool, and even when the throttling effect cannot be expected structurally.

Conventionally, as a means of absorbing the pulsation that occurs due to the large fluctuation range of the differential pressure, the pressure chamber in the mi control valve mechanism is formed large, and this is connected to the first pressure guiding hole and the second pressure guiding hole. A method is used in which a muffler effect is expected by combining it with There is no need to do so, and the control valve mechanism can be made more compact.

The present invention is constructed as described above, and includes a compression stroke pressure PH and a suction stroke pressure P+- as described above.
By synchronizing the patterns of pressure fluctuations that occur in the detection section of As a result, we have been able to stabilize the movement of the spool and prevent its malfunction.

[Brief explanation of drawings]

1 to 5 are drawings showing a first embodiment, in which FIG. 1 is a side sectional view of a slide vane compressor (cross sectional view taken along line A-B-C in FIG. 3), and FIG. The figure is a sectional view taken along the line DD in FIG. 1, FIG. 3 is a sectional view taken along lines F and E, and FIGS. 4 and 5 are sectional views showing the operating state of the control valve mechanism. 6 and 7 are drawings showing a second embodiment, in which FIG. 6 is a side sectional view of the scroll compressor, and FIG. 7 is a sectional view taken along the line FF in FIG. 6. Further, FIG. 8 is a graph diagram showing the variation range of the differential pressure according to the present invention, and FIG. 9 is a graph diagram showing the variation range of the differential pressure according to the conventional structure. (])Housing, (iA)Front housing, (
IB) rear housing, (2) cylinder block, (
3A) Front side plate, (3B) Rear sight plate, (4) Drive shaft, (5) Loco, (6) Compression chamber, (6a) (6b) (6c) (6d) Compression block, (7) Vane groove , (8) vane, (9) suction chamber, (9)' suction port, (10) suction hole, (marked bypass hole,
(12) control valve mechanism, (13) discharge chamber, (14) discharge hole, (15) discharge valve, (16) retainer-1 (17) separation chamber, (17) 'discharge port, (18) through hole, 09) Spool, (20) High pressure chamber, (21) Low pressure chamber, (22) Spring, (
23) First pressure hole, (24) second pressure hole, (231'(
2.1 pressure detection section, (31) housing, (32) front housing, (32a) front wall, (32b) peripheral wall, (33) rear housing, (33a) rear wall, (3
3b) Peripheral wall part, (34) partition panel, (34)' through hole, (
35) (351' suction chamber, (3G) compression action chamber, (37
) fixed scroll, (37a) base, (37b) scroll piece, (38) rotating scroll, (38a) base, <
3sb) Scroll piece, (39) bypass hole, (=I(
It suction port, (print bearing part, (42) drive shaft, (42 crankshaft, (1131 discharge chamber, G14) discharge port, (4)
5) Discharge hole, (45)'discharge valve, (4G) retainer-1
j47j control valve mechanism, (48) spool, (49) high pressure chamber, (50) low pressure chamber, 1) spring, 6 ■ first pressure guiding hole, trowel second pressure guiding hole, G'G■' pressure detection Department, Kasumi compression chamber, (5
5a) (55bH55c) (55d) (55e) Compressed block. Patent applicant Toyota Industries Corporation 2 ED Figure 2

Claims (3)

[Claims] (1) A compressor in which the compression chamber is divided into a plurality of compression blocks so as to be able to move continuously from the suction side to the discharge side, and the spool is opened and closed with respect to the bypass hole that communicates between the compression chamber and the suction chamber. The spool is biased in the opening direction, and a pair of pressure chambers are provided at both ends of the spool facing each other. The pressure detection section is provided so that it can face another compression block, and the surface pressure detection section is arranged in such a way that its phase is matched with respect to both compression blocks, and the pressure detection section on the low pressure side is placed in the initial stage of compression action. A variable capacity compressor installed facing the compression chamber. (2) A slide vane compressor in which the compression chamber is divided into a plurality of compression blocks by vanes provided so as to be freely protrusive and retractable toward the inside of the compression chamber from the rotor, and the surface pressure detection section detects the phase angle between each vane. The variable capacity compressor according to claim 1, wherein the variable capacity compressor is arranged with the same phase angle as. (3) With a fixed scroll and a rotating scroll that is provided to be able to swing and rotate with respect to the fixed scroll,
A scroll compressor in which a compression chamber is divided into a plurality of compression blocks, wherein the surface pressure detection parts are arranged in different compression blocks and arranged in series along the radial direction. The variable capacity compressor described.