JP4116334B2 - Compressor - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a compressor that adiabatically compresses a refrigerant that is interposed in a refrigeration cycle such as an air conditioner for a vehicle and that is vaporized in the refrigeration cycle. The present invention relates to a variable capacity compressor that controls the refrigerant discharge capacity.
[0002]
[Prior art]
In the compressor, a front housing is joined to a front end face of a cylinder block having a cylinder bore to form a crank chamber, and a rear housing is joined to a rear end face of the cylinder block via a valve plate, and a suction chamber and By forming a discharge chamber and converting the rotation of the drive shaft supported in the crank chamber into a reciprocating motion of the piston in the cylinder bore by a swash plate, the refrigerant gas in the suction chamber is sucked into the cylinder bore, compressed, and discharged Some discharge into the chamber. The discharge capacity is controlled by changing the inclination angle of the swash plate by controlling the pressure in the crank chamber by operating the control valve.
[0003]
FIG. 13 shows a rear housing used in a conventional small variable capacity compressor. The rear housing 101 is provided with a cylindrical partition wall 103 inside the outer peripheral leg portion 102, and is partitioned into a suction chamber 104 and a discharge chamber 105 by the partition wall 103. The control valve 106 is disposed so as to straddle the suction chamber 104 and the discharge chamber 105, and is held by a cylindrical holding wall 107 protruding from the suction chamber 104 and the discharge chamber 105. The holding wall 107 has a communication hole 108 with a crank chamber (not shown), a communication hole 109 with a suction chamber 104, and a communication port 110 with a discharge chamber 105 in order to enable pressure control by the control valve 106. , Provided by excavation with a bite.
[0004]
[Problems to be solved by the invention]
In recent years, this type of variable capacity compressor is increasingly required to be miniaturized, and in particular, a compressor mounted on a vehicle is strongly required to be miniaturized. Here, when the control valve 106 is disposed in the rear housing 101 as shown in FIG. 13, the volume of the suction chamber 104 and the discharge chamber 105 is limited by the control valve 106. As a result, the passage area is reduced and the passage resistance is increased. Along with this, smooth inhalation cannot be performed, and the compression efficiency tends to decrease. Conversely, if the compression efficiency is maintained, the required miniaturization cannot be realized.
[0005]
The present invention has been made on the basis of such a conventional technique, and has a structure in which a control valve is arranged in a rear housing forming a suction chamber and a discharge chamber, and the passage resistance of the suction chamber is increased while downsizing the compressor. It aims at providing the compressor which can be suppressed.
[0006]
[Means for Solving the Problems]
In the first aspect of the present invention, a front housing is joined to a front end face of a cylinder block having a cylinder bore to form a crank chamber, and a rear housing is joined to a rear end face of the cylinder block via a valve plate. A suction chamber and a discharge chamber are formed, and a piston is reciprocated using rotation of a drive shaft that is pivotally supported in the crank chamber, so that the supply air is in the middle of an air supply passage that communicates the discharge chamber and the crank chamber. A control valve for opening and closing the passage is provided, and the discharge capacity is controlled by adjusting the pressure in the crank chamber by operating the control valve, and the control valve extends over the suction chamber and the discharge chamber of the rear housing. In the arranged compressor,
A holding wall that protrudes from a partition wall that divides the suction chamber and the discharge chamber and covers the outer periphery of the control valve is provided so as to protrude only to the discharge chamber without being provided in the suction chamber, and the control valve is Provided exposed in the suction chamber ,
By forming a concave curved surface formed at substantially equal intervals along the outer peripheral surface of the control valve on the rear wall of the rear housing, a passage is formed between the concave curved surface and the outer peripheral surface of the control valve. The refrigerant flowing toward the control valve along the rear wall of the rear housing passes through the passage and flows directly along the rear wall of the rear housing .
[0007]
According to a second aspect of the present invention, in the compressor according to the first aspect, the control valve is an electromagnetic control valve that opens and closes a passage when a solenoid coil is energized.
[0008]
According to a third aspect of the present invention, in the compressor according to the second aspect, the electromagnetic control valve includes a solenoid coil at a position exposed to the suction chamber.
[0009]
【The invention's effect】
According to the first aspect of the present invention, since the control valve is exposed in the suction chamber, that is, the suction chamber has no holding wall for holding the control valve, the passage area of the suction chamber is increased. Therefore, even if the compressor is downsized, the passage resistance increase can be suppressed. Thereby, a small compressor with high compression efficiency can be provided.
[0010]
Here, the control valves include a mechanical control valve and an electromagnetic control valve that can be controlled externally. The latter electromagnetic control valve is used more often, but includes a solenoid coil, so it is compared with a mechanical control valve. The diameter size is large.
[0011]
According to the second aspect of the present invention, since the control valve is an electromagnetic control valve, the amount of protrusion of the holding wall required is larger than that of the mechanical control valve. large.
[0012]
According to the invention described in claim 3, in addition to the effect of the invention described in claim 2, since the control valve includes the solenoid coil at a position corresponding to the suction chamber, the solenoid coil is efficiently used by the refrigerant flowing through the suction chamber. Can be cooled. Therefore, an electromagnetic control valve can be designed without taking into consideration a decrease in magnetic force due to an increase in resistance value, and the electromagnetic control valve can be downsized. As a result, the compressor is further downsized.
[0013]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, a compressor according to an embodiment of the present invention will be described with reference to the drawings.
[0014]
FIG. 1 is an overall sectional view of a compressor according to a first embodiment of the present invention, FIG. 2 is a rear view of the rear housing of the compressor, and FIG. 3 is a front view of the rear housing of the compressor. FIG. 4 is a front view of a rear housing equipped with a control valve, FIG. 5 is an enlarged cross-sectional view of the rear housing of the compressor, and FIG. 6 is a diagram for explaining a process of forming the rear housing. 7 is an enlarged cross-sectional view of the control valve, FIG. 8 is a schematic view showing a portion where the control valve is exposed in the suction chamber, and FIG. 9 is a cross-sectional view taken along the line SA-SA in FIG.
[0015]
The compressor 1 according to the first embodiment is a swash plate type variable capacity compressor, which is used, for example, in a cooling cycle of a vehicle air conditioner and adiabatically compresses refrigerant gas evaporated in a refrigeration cycle.
[0016]
The variable capacity compressor 1 includes a cylinder block 2 having a plurality of cylinder bores 3 arranged at equal intervals in the circumferential direction, and a crank chamber 5 between the cylinder block 2 joined to the front end face of the cylinder block 2. And a rear housing 6 joined to the rear end surface of the cylinder block 2 via a valve plate 9 to form a suction chamber 7 and a discharge chamber 8. The cylinder block 2, the front housing 4 and the rear housing 6 are fastened and fixed by a plurality of through bolts B.
[0017]
The valve plate 9 includes a suction hole 11 that communicates the cylinder bore 3 and the suction chamber 7, and a discharge hole 12 that communicates the cylinder bore 3 and the discharge chamber 8.
[0018]
A valve mechanism (not shown) for opening and closing the suction hole 11 is provided on the cylinder block 2 side of the valve plate 9, while a valve mechanism (not shown) for opening and closing the discharge hole 12 is provided on the rear housing 6 side of the valve plate 9. Is provided. A gasket is interposed between the valve plate 9 and the rear housing 6 to keep the suction chamber 7 and the discharge chamber 8 sealed. Further, an O-ring is interposed on the peripheral edge of the valve plate 9 at the joint surface between the rear housing 6 and the cylinder block 2 to prevent refrigerant leakage to the outside of the compressor 1.
[0019]
A drive shaft S is pivotally supported through bearings in the support holes 19 and 20 in the center of the cylinder block 2 and the front housing 4, and the drive shaft S is rotatable in the crank chamber 5.
[0020]
In the crank chamber 5, a drive plate 21 fixed to the drive shaft S, a journal 24 slidably connected by a pin 23 to a sleeve 22 slidably fitted to the drive shaft S, and the journal 24 And a wobble plate (swash plate) 26 attached to the boss portion 25 via a bearing. The wobble plate 26 is slidably connected to a restriction plate 35 fixed in the crank chamber 5, thereby preventing rotation and swinging in the axial direction. That is, when the journal 24 rotates by rotating the drive shaft S, the wobble plate 26 swings non-rotatingly and in the axial direction as the journal 24 rotates and swings. The drive plate 21 and the journal 24 are connected to the hinge arms 21h and 24h via arcuate long holes 27 and pins 28, whereby the wobbling plate 26 has a maximum inclination angle and a minimum inclination angle. Is regulated.
[0021]
The pistons 29 accommodated in the respective cylinder bores 3 are connected to the wobble plate 26 via the piston rod 30 and reciprocate when the wobble plate 26 swings. The basic function of the compressor 1 is to compress the refrigerant sucked into the suction chamber 7 → the valve hole 9 of the valve plate 9 → the cylinder bore 3 by the piston movement of the piston 29, and the cylinder bore 3 → the discharge hole 12 of the valve plate 9 → The liquid is discharged into the discharge chamber 8.
[0022]
In order to make this discharge capacity variable, an extraction passage 31 that always connects the crank chamber 5 and the suction chamber 7, an air supply passage 32 that connects the crank chamber 5 and the discharge chamber 8, and the air supply passage 32 A pressure control mechanism including a control valve 33 that opens and closes is provided (see FIG. 7). When the pressure in the crank chamber 5 is changed by opening and closing the control valve 33, the inclination angle of the wobble plate 26 changes due to the pressure balance between the crank chamber 5 and the suction chamber 7 (pressure balance before and after the piston 29). The piston stroke changes and the discharge capacity of the compressor 1 changes.
[0023]
The bleed passage 31 includes the support hole 19 of the cylinder block 2, the passage 31c of the valve plate 9, the passage 31a of the rear housing 6, the groove 31b of the rear housing, and the passage 31a of the rear housing 6. The air supply passage 32 includes a cylinder block passage 32 a, a valve plate passage 32 b, a passage 32 c in the rear housing 6, an annular space 57, and a passage 59 in the control valve 33.
[0024]
2 to 5 show the rear housing 6.
[0025]
The rear housing 6 defines a cylindrical partition wall 36, a discharge chamber 8 is formed on the inner peripheral side, and a suction chamber 7 is formed on the outer peripheral side. A suction port 37 that communicates with the chamber 7 via a passage 38 and a discharge port 39 that communicates with the discharge chamber 8 via a passage 40 are provided. The suction port 37 is connected to a low-pressure side pipe that communicates with the evaporator, and the discharge port 39 is connected to a high-pressure side pipe that communicates with a capacitor.
[0026]
The rear housing 6 is provided with a projecting wall 44 that projects from the partition wall 36 toward the discharge chamber 8 and forms a heat insulating space 43 between the rear wall 6 and the partition wall 36. The heat of the refrigerant thus formed is difficult to be transmitted to the suction chamber 7 through the partition wall 36.
[0027]
A rib 50 is provided on the rear wall of the rear housing 6 for the purpose of reinforcing the rear housing 6. Generally, this type of rib tends to cause a turbulent flow of the circulating refrigerant. The rib 50 according to the embodiment includes inclined surfaces 50a and 50b that are inclined from the proximal end toward the distal end, and is configured to have a tapered cross section. Thereby, generation | occurrence | production of a vortex | eddy_current is suppressed. Further, the reinforcing action by the ribs is also improved.
[0028]
The rear housing 6 is provided with a control valve 33 extending over the suction chamber 7 and the discharge chamber 8. The control valve 33 is provided with an insertion opening 51 provided at the outer peripheral leg and an inner periphery of the cylindrical holding wall 41. The surface 42 is held via O-rings 52, 53, 54. The holding wall 41 is provided so as to project only in the discharge chamber 8 and is not provided in the suction chamber 7. That is, the control valve 33 is completely exposed to the suction chamber 7. Therefore, unlike the prior art shown in FIG. 13, unlike the structure in which the holding wall 107 for holding the control valve 106 is provided so as to protrude from the suction chamber 104 and the discharge chamber 105, the passage area of the suction chamber 104 is limited. The passage area of the suction chamber 7 can be secured widely.
[0029]
The holding wall 41 is configured such that the upper opening 55 faces the discharge chamber 8 and the lower opening 56 of the holding wall 41 faces the suction chamber 7, and the inner periphery of the holding wall 41 is formed by the O ring 52 and the O ring 53. An annular space 57 generated between the surface 42 and the outer peripheral surface of the control valve 33 is defined, and the annular space 57 is a part of the air supply passage 32. A region between the O-ring 53 and the O-ring 54 is a part of the suction chamber 7, and a solenoid coil 62 (described later) of the control valve 33 is disposed in this region. The heat generated by the solenoid coil 62 can be efficiently cooled.
[0030]
The manufacturing process of the rear housing 6 will be described. In the manufacturing of the rear housing 6, first, an original shape as shown in FIG. 6 is formed by die casting, and then the holding hole 42, the passage 31a, and the passage are formed on the die casting original shape by a predetermined bite. 32c, the suction port 37, the passage 38, the discharge port 39, the passage 40, and the like are excavated to obtain the required rear housing 6 shown in FIG. Here, in the embodiment, the holding wall 41 is provided only in the discharge chamber 8 so as not to be provided in the suction chamber 7, so that the communication provided in the holding wall 107 as in the prior art shown in FIG. Since the hole 109 need not be excavated, there is an advantage that the number of excavation steps can be reduced.
[0031]
Hereinafter, the configuration of the control bubble 33 will be described in detail.
[0032]
The control valve 33 of this embodiment is an electromagnetic control valve, and as shown in FIG. 7, the supply path 32 provided in the case 58 including the first case 58a and the second case 58b and the second case 58b. A passage 59 constituting part of the valve body, a valve body 61 that opens and closes a valve port 60 provided in the passage 59, and a magnetic force that is accommodated in the first case 58a and opens and closes the valve body 61. And a solenoid coil 62.
[0033]
The upper opening of the first case 58a that houses the solenoid coil 62 is closed by the diaphragm 63 and sealed from the refrigerant. The first case 58a accommodates the solenoid coil 62 and an actuator 64 that can be moved by the magnetic force of the solenoid coil 62. On the other hand, the second case 58b fixed to the upper end of the first case 58a contains the above-described actuator. A needle 65 provided integrally with the valve body 61 and disposed on the actuator 64 via the diaphragm 63 is provided so that the valve body 61 can be moved by the magnetic force of the solenoid coil 62 by the actuator 64 and the needle 65. It has become. Above the valve body 61, a spring 66 for biasing a spring force that presses the valve body 61 in the valve closing direction is provided. On the other hand, below the actuator 64, a spring that presses the valve body 61 in the valve opening direction. A spring 67 that biases the force is provided.
[0034]
The opening degree of the valve body 61 is adjusted by generating a magnetic force in the solenoid coil 62 by a signal from an auto amplifier (not shown) generated based on the outside air temperature, the room temperature, the amount of solar radiation, and the like. Specifically, the opening is adjusted as follows.
[0035]
When the thermal load in the refrigeration cycle is small, the auto amplifier determines that the cooling capacity may be small, and outputs a signal for reducing the current value or the duty ratio flowing through the solenoid coil 62. Along with this signal, the magnetic force acting downward on the actuator 64 decreases, and the needle 65 on the diaphragm 63 is pushed up by the spring force of the spring 67, and the valve body 61 moves in the valve opening direction. As a result, a part of the high-pressure refrigerant (discharge pressure Pd) compressed by the piston 29 is introduced into the crank chamber 7 from the discharge chamber 7 through the air supply passage 32, and the internal pressure of the crank chamber 5 (crank chamber pressure Pc). Is increased. When the crank chamber pressure Pc is slightly larger than the suction chamber pressure Ps, the inclination angle of the wobble plate 26 around the pin 23 is decreased, the compression stroke is shortened, and the amount of discharged refrigerant is reduced, so that the inside of the refrigeration cycle is reduced. The refrigerant circulation amount that circulates is reduced, and an appropriate refrigerant amount corresponding to a low heat load is obtained.
[0036]
On the other hand, when the heat load of the refrigeration cycle is large, the auto-amplifier determines that the required cooling capacity is large, and outputs a signal for increasing the value of the current flowing through the solenoid coil 62 or the duty ratio. Along with this signal, the magnetic force acting downward on the actuator 64 increases, the needle 65 on the diaphragm 63 is pushed down against the spring force of the spring 67, and the valve body 61 moves in the valve closing direction. As a result, the high-pressure refrigerant (discharge pressure Pd) compressed by the piston 29 is not introduced into the crank chamber 5 but gradually flows by the refrigerant that gradually flows from the crank chamber 5 to the suction chamber 7 through the extraction passage 31 (always communicating passage). The crank chamber pressure Pc and the suction chamber pressure Ps are balanced. When the crank chamber pressure Pc and the suction chamber pressure Ps are equal, the inclination angle of the wobble plate 26 is maximized by the moment force acting on the wobble plate 26, and the compression stroke is maximized. Therefore, when compressed in this state, the amount of refrigerant circulating in the refrigeration cycle increases due to the increase in the amount of refrigerant discharged, and the refrigerant amount is appropriate for a large heat load.
[0037]
Here, the control valve 33 is provided with a low pressure side pressure chamber 69 communicating with the suction chamber 7 through the passage 68 on the upper surface side of the diaphragm 63, while being opened to the atmosphere through the passage 70 on the lower surface side of the diaphragm 63. When the atmospheric chamber 71 is provided and the auto amplifier is OFF, the valve body 61 is supplied by the balance of the pressure of the atmospheric chamber 71, the pressure of the low pressure chamber 69, the pressing force of the spring 66, and the pressing force of the spring 67. The passage 31 is opened and closed so that the pressure on the evaporator side is kept constant. Note that the pressures in the atmospheric chamber 71 and the low pressure chamber 69 are also taken into account when the auto amplifier is turned on and the magnetic force of the solenoid coil 62 is acting.
[0038]
As described above, according to the compressor 1 of the first embodiment, the control valve 33 is held by the holding wall 41 provided so as to protrude only in the discharge chamber 8, and the control valve 33 is exposed to the suction chamber 7. Since it is provided, the passage area of the suction chamber 7 can be enlarged. For this reason, even if the compressor 1 is reduced in size, a reduction in the passage area of the suction chamber 7 can be avoided, and an increase in passage resistance can be suppressed. Thereby, the small compressor 1 with high compression efficiency can be provided.
[0039]
Further, since the holding wall 41 extends only in the discharge chamber 8 and is not provided in the suction chamber 7, a communication hole (corresponding to reference numeral 109 in FIG. 13) for connecting the suction chamber 7 and the low-pressure side pressure chamber 69 is provided. There is also an advantage that the number of excavation steps can be reduced.
[0040]
In addition, when the electromagnetic control valve 33 having a larger diameter than the mechanical type is provided as in the first embodiment, the effective passage area in the rear housing 6 is limited, so that the control valve 33 is exposed in the suction chamber 7. The effect of making it great.
[0041]
Further, according to the compressor 1 of the first embodiment, since the solenoid coil 62 is provided at a position corresponding to the suction chamber 7, the solenoid coil 62 can be efficiently cooled by the refrigerant flowing through the suction chamber 7. Therefore, the electromagnetic control valve 33 can be designed without taking into consideration a decrease in magnetic force due to an increase in resistance value, and the electromagnetic control valve 33 can be downsized. As a result, the compressor 1 is further reduced in size.
[0042]
Second Embodiment: FIGS. 10 to 12 show a second embodiment according to the present invention. FIG. 10 is a view showing a front end surface of the rear housing of the second embodiment, FIG. 11 is a sectional view of the rear housing, and FIG. 12 is a sectional view of a control valve of the second embodiment. In addition, about the structure similar to 1st Embodiment, the same code | symbol is attached | subjected and description of a structure and an effect is abbreviate | omitted.
[0043]
The second embodiment is different from the first embodiment in that a mechanical control valve 80 is used, and the control valve 80 is held by a holding wall 41 provided so as to protrude only in the discharge chamber 8 and is completely in the suction chamber 7. This is similar to the first embodiment in that it is exposed. Therefore, according to the second embodiment, a small compressor with high compression efficiency can be provided as in the first embodiment.
[0044]
The mechanical control valve 80 of this embodiment has the following configuration. As shown in FIG. 12, the control bubble 80 includes a case 81 including a first case 81a and a second case 81b, a passage 82 provided in the first case 81a and constituting a part of the air supply passage 32, and the passage. 82, a valve body 84 that opens and closes a valve port 83, a needle 85 having the valve body 84, a rod 86 connected to the needle 85, and the valve body 84 via the rod 86 and the needle 85. And a bellows 87 to be moved.
[0045]
The upper opening of the second case 81b is closed by the lower end of the first case 81a, and the rod 86 and the bellulose 87 are accommodated in the second case 81b. The internal space 88 of the second case 81 b communicates with the suction chamber 7 through the through-hole 89 to form a low pressure side pressure chamber. The bellows 87 in the low pressure side pressure chamber 88 has the same or equivalent pressure as the atmosphere, and the bellows 87 is an atmosphere chamber 90. The valve body 81 is energized with a spring force that moves in the valve closing direction from the springs 91 and 92 and is energized with a spring force that moves in the valve opening direction from the spring 93. The valve body 84 opens and closes the air supply passage 32 through the rod 86 and the needle 85 due to the pressure fluctuation, so that the pressure on the evaporator side is kept constant.
[0046]
As described above, according to the present invention, since the control valve is provided exposed to the suction chamber, the passage area of the suction chamber can be enlarged. That is, according to the present invention, it is possible to provide a small compressor having high compression efficiency, which has been difficult in the past.
[0047]
In the above-described embodiment, the discharge chamber 8 is provided on the inner peripheral side of the partition wall 36 and the suction chamber 7 is provided on the outer peripheral side. However, in the present invention, the suction chamber is disposed on the inner peripheral side. Needless to say, this can also be applied to a structure provided on the outer peripheral side.
[Brief description of the drawings]
FIG. 1 is an overall cross-sectional view of a compressor according to a first embodiment of the present invention.
FIG. 2 is a rear view of the rear housing of the compressor.
FIG. 3 is a front view of a rear housing of the compressor.
FIG. 4 is a front view of a rear housing equipped with a control valve.
FIG. 5 is an enlarged sectional view of a rear housing, which is a main part of the compressor.
FIG. 6 is a cross-sectional view for explaining a rear housing forming process and showing a rear housing casting original form.
FIG. 7 is an enlarged cross-sectional view of the control valve. FIG. 8 is a schematic view showing a portion where the control valve is exposed in the suction chamber.
9 is a cross-sectional view taken along the line SA-SA in FIG.
FIG. 10 is a view showing a front end surface of a rear housing according to a second embodiment.
FIG. 11 is a cross-sectional view of the rear housing.
FIG. 12 is a cross-sectional view of a control valve of a second embodiment.
FIG. 13 is a view showing a conventional example of a rear housing.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 Variable capacity compressor 2 Cylinder block 3 Cylinder bore 4 Front housing 5 Crank chamber 6 Rear housing 7 Suction chamber 8 Discharge chamber 29 Piston 32 Air supply passage 33 Electromagnetic control valve (control valve)
36 Partition wall 36a Front end surface 42 of partition wall Holding wall 80 Mechanical control bubble (control valve)
S drive shaft

Claims (3)

A front housing (4) is joined to a front end face of a cylinder block (2) having a cylinder bore (3) to form a crank chamber (5), and a valve plate (9) is attached to a rear end face of the cylinder block (2). ) To form the suction chamber (7) and the discharge chamber (8) by using the rotation of the drive shaft (S) supported in the crank chamber (5). Reciprocating the piston (29),
Control valves (33, 80) for opening and closing the air supply passage (32) are provided in the middle of the air supply passage (32) communicating the discharge chamber (8) and the crank chamber (5). (33, 80) is operated to adjust the pressure in the crank chamber (5) to control the discharge capacity,
In the compressor (1) in which the control valve (33, 80) is disposed so as to straddle the suction chamber (7) and the discharge chamber (8) of the rear housing (6),
A holding wall (42) that protrudes from a partition wall (36) that partitions the suction chamber (7) and the discharge chamber (8) and covers the outer periphery of the control valve (33, 80) is provided with the suction chamber ( 36). 7) without being provided in the discharge chamber (8), the control valve (33, 80) is provided exposed to the suction chamber (7) ,
By forming concave curved surfaces (6b) formed at substantially equal intervals along the outer peripheral surface of the control valve (33, 80) on the rear wall of the rear housing (6), the concave curved surfaces (6b) and A refrigerant (P) is formed between the control valve (33, 80) and the outer peripheral surface of the control valve (33, 80), and flows toward the control valve (33, 80) along the rear wall of the rear housing (6). Passes through the passage (P) and flows as it is along the rear wall of the rear housing (6 ). Compressor (1) according to claim 1,
The compressor (1), wherein the control valve (33) is an electromagnetic control valve (33) for opening and closing an air supply passage (32) by energization of a solenoid coil (62). Compressor (1) according to claim 2,
The compressor (1), wherein the electromagnetic control valve (33) includes a solenoid coil (62) at a position exposed to the suction chamber (7).

Images