JP5963544B2 - Gas compressor - Google Patents

Description

  The present invention relates to a gas compressor, and more particularly to an improvement of a vane rotary type gas compressor.

  For example, vehicles such as automobiles are provided with an air conditioner for adjusting the temperature in the passenger compartment. Such an air conditioner has a loop-shaped refrigerant cycle in which refrigerant (cooling medium) is circulated, and this refrigerant cycle is provided with an evaporator, a compressor, a condenser, and an expansion valve in this order. Yes.

  The compressor (compressor) of the air conditioner compresses the gaseous refrigerant (refrigerant gas) evaporated by the evaporator into a high-pressure refrigerant gas and sends it to the condenser.

  As such a compressor, a rotor having a plurality of vanes provided so as to protrude and be housed in a cylinder having a substantially elliptical inner peripheral surface, the tip of which is slidably in contact with the inner peripheral surface of the cylinder has been rotated. A vane rotary type compressor that is freely supported is known (for example, see Patent Document 1).

  This vane rotary type compressor has a compression chamber whose volume changes due to sliding contact with the inner circumferential surface of the rotating vane as the rotor rotates, and through the suction port as the volume of the compression chamber increases. The refrigerant gas is sucked in, the sucked refrigerant gas is compressed as the volume of the compression chamber decreases, and the high-pressure refrigerant gas is discharged into the discharge chamber through the discharge port. Then, high-pressure refrigerant gas is sent from the discharge chamber to the condenser side.

  The vane is slidably disposed in a slit-like vane groove exposed on the surface from the inside of the rotor. And this vane protrudes from the rotor surface by the back pressure (vane back pressure) by the oil supplied to the bottom of the vane groove through the vane back pressure space and the centrifugal force of the rotating rotor, and the tip of the vane Is maintained in contact with the inner peripheral surface of the cylinder.

JP 54-28008 A

  By the way, in a vane rotary type compressor, since the refrigerant gas is rapidly compressed, overcompression is likely to occur in the compression chamber, and accordingly, power loss is increased or the pressure difference between adjacent compression chambers is increased. From other types of gas compressors (for example, rotary piston type compressors) due to the leakage of refrigerant gas compressed from the compression chamber downstream in the rotation direction to the compression chamber upstream in the rotation direction. However, the efficiency (coefficient of performance or COP (Coefficient of Performance)) tended to be low.

  The present invention has been made in view of the above circumstances, and an object of the present invention is to provide a gas compressor capable of preventing the occurrence of over-compression in a compression chamber.

In order to solve the above-mentioned problems, an invention according to claim 1 is directed to a substantially columnar rotor that rotates integrally with a rotation shaft, and an inner periphery having a contour shape that surrounds the rotor from the outside of the outer peripheral surface of the rotor. A cylinder having a surface, a plurality of plate-like vanes provided in a vane groove formed in the rotor so as to protrude from an outer peripheral surface of the rotor toward an inner peripheral surface of the cylinder, and both ends of the rotor and the cylinder Each of the two side blocks, and the vane forms a plurality of compression chambers by partitioning a space formed between the inner peripheral surface of the cylinder and the outer peripheral surface of the rotor, Each of the formed compression chambers is a gas compressor in which the contour shape of the inner peripheral surface of the cylinder is set so that the medium is sucked, compressed, and discharged for only one cycle during one rotation of the rotor. , Along the circumferential direction of the inner circumferential surface of the cylinder, the inner circumferential surface of the cylinder and the outer circumferential surface of the rotor are closest to each other in a range of one round around the axis of the rotating shaft. It has at least two discharge holes for discharging the medium compressed in the compression chamber to the upstream side in the rotation direction, and the closest areas are the inner peripheral surface of the cylinder and the outer peripheral surface of the rotor And the inner circumference of the cylinder in such a manner that it is biased to the downstream side in the rotation direction of the rotor in a region farthest from the rotation center of the rotor, in a region farthest from one rotation around the rotation axis. The contour shape of the surface is set, and among the discharge holes, at least the first discharge hole located on the side closest to the closest region is formed in one of the side blocks, and the first The discharge hole extends from the end face of the cylinder It is characterized in that it is formed so as to face across the end face of the rotor.

  In the gas compressor according to claim 2, the second discharge hole is formed in one of the side blocks so as to be positioned upstream of the first discharge hole in the rotation direction of the rotor. It is characterized by that.

According to a third aspect of the present invention, there is provided a discharge valve that opens and closes the discharge hole by elastic deformation only around the second discharge hole, and the discharge valve is excessively warped by a discharged medium. It is characterized in that the valve support to prevent is provided.

  Further, in the gas compressor according to claim 4, the medium compressed in the compression chamber is formed on the outer surface side of the side block through the first and second discharge holes formed in one of the side blocks. It is characterized by being discharged into the discharge chamber.

  The gas compressor according to the present invention has at least two discharge holes including the first discharge holes formed in one of the side blocks, so that the medium compressed in the compression chamber through these discharge holes Can be prevented from being overcompressed.

1 is a longitudinal sectional view showing a gas compressor (vane rotary type gas compressor) according to an embodiment of the present invention. AA sectional view taken on the line AA of FIG. The external view which looked at the rear side block from the discharge chamber side. BB sectional drawing of FIG.

  Hereinafter, the present invention will be described based on the illustrated embodiments. FIG. 1 is a longitudinal sectional view showing a vane rotary type gas compressor (hereinafter referred to as “compressor”) which is an embodiment of the gas compressor according to the present invention, and FIG. 2 is taken along line AA in FIG. It is a figure which shows the cross section along. Note that the compressor of the present embodiment is an electric type that incorporates an electric motor.

(Overall configuration and operation of compressor 1)
The illustrated compressor 100 is configured, for example, as a part of an air conditioning system (hereinafter referred to as an “air conditioning system”) that performs cooling by using the heat of vaporization of a cooling medium, and condensing that is another component of the air conditioning system. It is provided on the circulation path of the cooling medium together with a condenser, an expansion valve, an evaporator, etc. (all not shown). In addition, as such an air conditioning system, the air conditioning apparatus for adjusting the temperature in the vehicle interior of a vehicle (automobile etc.) is mentioned, for example.

  The compressor 100 compresses the refrigerant gas as a gaseous cooling medium taken from the evaporator of the air conditioning system, and supplies the compressed refrigerant gas to the condenser of the air conditioning system. The condenser liquefies the compressed refrigerant gas and sends it to the expansion valve as a high-pressure liquid refrigerant. The high-pressure and liquid refrigerant is reduced in pressure by the expansion valve and sent to the evaporator. The low-pressure liquid refrigerant absorbs heat from ambient air and vaporizes in the evaporator, and cools the air around the evaporator by heat exchange with the heat of vaporization.

  As shown in FIG. 1, the compressor 100 has a configuration in which a motor 90 and a compressor main body 60 are accommodated in a housing 10 mainly composed of a main body case 11 and a front cover 12.

  The main body case 11 has a substantially cylindrical shape, and is formed such that one end (right side in FIG. 1) of the cylindrical shape is closed, and the other end (left side in FIG. 1) is open. Has been.

  The front cover 12 is formed in a lid shape so as to close the opening while being in contact with the opening-side end portion of the main body case 11. In this state, the front cover 12 is fastened to the main body case 11 by a fastening member. And a housing 10 having a space inside is formed.

  The front cover 12 is formed with a suction port 12a for introducing a low-pressure refrigerant gas G1 into the suction chamber 13 from the evaporator of the air conditioning system. On the other hand, a discharge port 11a for discharging the high-pressure refrigerant gas G2 obtained in the compressor main body 60 to the condenser of the air conditioning system is formed in the discharge chamber 14 described later of the main body case 11.

  The motor 90 provided inside the main body case 11 constitutes a multiphase brushless DC motor including a permanent magnet rotor 90a and an electromagnet stator 90b. The stator 90b is fitted and fixed to the inner peripheral surface of the main body case 11, and the rotating shaft 51 is fixed to the rotor 90a.

  The motor 90 drives the rotor 90a and the rotating shaft 51 to rotate around the axis by exciting the electromagnet of the stator 90b with the electric power supplied via the power connector 90c attached to the end face of the front cover 12. Let

  A configuration including an inverter circuit 90d or the like may be employed between the power connector 90c and the stator 90b.

  Although the compressor 100 of the present embodiment is an electric one as described above, the gas compressor according to the present invention is not limited to an electric one, and may be a mechanical one. If the compressor 100 of the embodiment is mechanical, instead of providing the motor 90, the rotating shaft 51 protrudes from the front cover 12 to the outside, and the front end of the protruding rotating shaft 51 has a vehicle engine. What is necessary is just to set it as the structure provided with the pulley, the gearwheel, etc. which receive motive power transmission from these.

  The compressor main body 60 accommodated in the housing 10 together with the motor 90 is arranged side by side with the motor 90 along the direction in which the rotating shaft 51 extends, and is inserted into the main body case 11 by a fastening member 15 such as a bolt. It is fixed.

  The compressor body 60 includes the rotating shaft 51 rotated by the motor 90, a substantially cylindrical rotor 50 that rotates integrally with the rotating shaft 51, and the rotor 50 outside the outer peripheral surface 50a (see FIG. 2). A cylinder 40 having a contour-shaped inner peripheral surface 40a surrounding from the side, five plate-like vanes 58 provided so as to protrude from the outer peripheral surface 50a of the rotor 50 toward the inner peripheral surface 40a of the cylinder 40, and the rotor 50 and two side blocks (front side block 20 and rear side block 30) that block both ends of the cylinder 40 are provided.

  The rotating shaft 51 is rotatably supported by bearings 12 b formed on the front cover 12 and bearings 27 and 37 formed on the side blocks 20 and 30 of the compressor body 60, respectively.

  On the outer peripheral surfaces of the front side block 20 and the rear side block 30, sealing members such as O-rings are installed over the entire outer periphery, and the discharge chamber is formed in the main body case 11 on the rear side block 30 side. 14 and the main body case 11 on the front side block 20 side and the suction chamber 13 formed in the front cover 12 are partitioned with good airtightness.

  An oil separator 70 is attached to the outer surface of the rear side block 30 so as to be positioned in the discharge chamber 14. The motor 90 is provided in the suction chamber 13 formed in the front cover 12.

  As shown in FIG. 2, a single cylinder chamber 42 is formed in the compressor body 60 between the inner peripheral surface 40 a of the cylinder 40, the outer peripheral surface 50 a of the rotor 50, and both side blocks 20 and 30. ing.

Specifically, the outer peripheral surface 50a of the inner circumferential surface 4 0 a rotor 50 of the cylinder 40, one rotation about the axis of the rotary shaft 51 only one place in the range of (angle 360 degrees) closest (in FIG. 2 The contour shape of the inner peripheral surface 40a of the cylinder 40 is set so that the proximity portion 48), and the cylinder chamber 42 thereby forms a single space.

  Note that, in the contour shape of the inner peripheral surface 40a of the cylinder 40, the proximity portion 48, which is the region where the inner peripheral surface 40a of the cylinder 40 and the outer peripheral surface 50a of the rotor 50 are closest to each other, is located in the vicinity of the inner peripheral surface 40a of the cylinder 40 and the rotor. In this embodiment, the remote portion 49 is located at a position away from the remote portion 49, which is the farthest area from the outer peripheral surface 50a of the 50, along the rotational direction W (clockwise direction in FIG. 2) of the rotor 50 at an angle of about 270 degrees. Is formed.

  The contour shape of the inner peripheral surface 40a of the cylinder 40 is such that the distance between the outer peripheral surface 50a of the rotor 50 and the inner peripheral surface 40a of the cylinder 40 is monotonous from the remote portion 49 to the proximity portion 48 along the rotation direction W. The shape is set to decrease.

  The vane 58 is slidably fitted in a vane groove 59 formed in the rotor 50, and protrudes outward from the outer peripheral surface 50 a of the rotor 50 by back pressure due to refrigerating machine oil supplied to the vane groove 59.

  The vane 58 divides the single cylinder chamber 42 into a plurality of compression chambers 43, and one compression chamber 43 is formed by two vanes 58 that move back and forth along the rotation direction W of the rotor 50. . Therefore, in the present embodiment in which five vanes 58 are installed around the rotation shaft 51 at equal angular intervals of 72 degrees, five compression chambers 43 are formed.

  More specifically, when the vane 58 is located on the upstream side or the downstream side in the rotation direction of the rotor 50 with respect to the proximity portion 48 of the cylinder chamber 42, the space between the vane 58 and the proximity portion 48 is not limited. In addition, a small compression chamber having a small volume is further formed.

  The internal volume of the compression chamber 43 obtained by partitioning the cylinder chamber 42 with the vane 58 monotonously decreases along the rotation direction W until the compression chamber 43 reaches the proximity portion 48 from the remote portion 49.

  A suction hole 23 that is formed in the front side block 20 and communicates with the suction chamber 13 faces a portion on the downstream side in the rotation direction of the rotor 50 with respect to the proximity portion 48 of the cylinder chamber 42.

  2, the rear side block 30 is formed with two first discharge holes 31a and second discharge holes 31b along the circumferential direction of the inner peripheral surface of the cylinder 40. Almost half of the first and second discharge holes 31a and 31b face the vicinity of the upstream portion in the rotation direction of the rotor 50 with respect to the proximity portion 48 of the cylinder chamber 42 (the first and second discharge holes 31a and 31b). Details of 31b will be described later). FIG. 3 is an external view of the first and second discharge holes 31a and 31b when the rear side block 30 is viewed from the discharge chamber 14 side. In FIG. 3, the oil separation portion 70 attached to the outer surface of the rear side block 30 is removed.

  In each compression chamber 43, during one rotation of the rotor 50, the refrigerant gas is sucked through the suction hole 23, the refrigerant gas is compressed, and the refrigerant gas is discharged into the first and second discharge holes 31a and 31b in one cycle. The contour shape of the inner peripheral surface 40a of the cylinder 40 is set so as to perform only. The first discharge hole 31a is closer to the proximity portion 48 along the rotation direction W of the rotor 50, and is located upstream of the first discharge port 31a along the rotation direction W of the rotor 50. Two discharge holes 31b are formed.

  On the upstream side in the rotational direction of the rotor 50 with respect to the remote portion 49 of the cylinder chamber 42, the cylinder 40 has a gap so that the distance between the inner peripheral surface 40 a of the cylinder 40 and the outer peripheral surface 50 a of the rotor 50 increases rapidly from a small state. The contour shape of the inner peripheral surface 40 a is set, and in the angle range including the remote portion 49, the volume of the compression chamber 43 increases as the rotor 50 rotates in the rotation direction W, and the compression chamber 43 passes through the suction hole 23. This is a stroke (intake stroke) in which the refrigerant gas is sucked.

  Next, the cylinder 40 is arranged such that the distance between the inner peripheral surface 40a of the cylinder 40 and the outer peripheral surface 50a of the rotor 50 gradually decreases toward the downstream side in the rotation direction of the rotor 50 with respect to the remote portion 49 of the cylinder chamber 42. A contour shape of the inner peripheral surface 40a is set, and in that range, the volume of the compression chamber 43 decreases with the rotation of the rotor 50, and the stroke in which the refrigerant gas in the compression chamber 43 is compressed (compression stroke) Become.

  Further, on the downstream side in the rotation direction of the rotor 50 with respect to the remote portion 49 of the cylinder chamber 42, the interval between the inner peripheral surface 40a of the cylinder 40 and the outer peripheral surface 50a of the rotor 50 is further reduced, and the compression of the refrigerant gas further proceeds. When the pressure of the refrigerant gas reaches the discharge pressure, the high-pressure refrigerant gas is discharged into the first and second discharge holes 31a and 31b of the rear side block 30 (discharge stroke).

  As the rotor 50 rotates, each of the compression chambers 43 repeats the suction stroke, the compression stroke, and the discharge stroke in this order, so that the low-pressure refrigerant gas sucked from the suction chamber 13 becomes a high pressure. Discharge from the main body 60.

  As shown in FIG. 4, around the second discharge hole 31 b formed in the rear side block 30, the refrigerant gas in the compression chamber 43 in the compression stroke warps toward the discharge chamber 14 when the pressure exceeds a predetermined pressure. The discharge valve 32 that elastically deforms to open the second discharge hole 31b and closes the second discharge hole 31b by elastic force when the refrigerant gas pressure does not reach the predetermined pressure, and the discharge valve 32 A valve support 33 is installed to prevent excessive warpage on the discharge chamber 14 side.

  In FIG. 3, the discharge valve 32 and the valve support 33 are not shown, and only the discharge ports 31a and 31b are shown. Moreover, the discharge valve and the valve support are not provided around the first discharge hole 31a. This is because the first discharge hole 31a discharges the high-pressure refrigerant gas compressed from the second discharge hole 31b side to the discharge chamber 14 during operation, so that the refrigerant gas flows backward from the discharge chamber 14. This eliminates the need for a discharge valve and valve support.

  The first and second discharge holes 31a and 31b are connected to an oil separation portion 70 attached to the outer surface of the rear side block 30 (the surface facing the discharge chamber 14) via a connected discharge passage (not shown). Communicates.

  The oil separator 70 is used for refrigerating machine oil mixed with refrigerant gas (vane back pressure oil leaked into the cylinder chamber 42 (compression chamber 43) from the vane groove 59 formed in the rotor 50 holding the vane 58 so as to protrude). The refrigerant gas is separated from the refrigerant gas, and the high-pressure refrigerant gas discharged through the first and second discharge holes 31a and 31b and introduced through the discharge passage (not shown) is spirally swirled. Centrifuge the refrigeration oil.

  The refrigerating machine oil R (see FIG. 1) separated from the refrigerant gas is accumulated at the bottom of the discharge chamber 14, and the high-pressure refrigerant gas G2 after the refrigerating machine oil R is separated passes through the discharge port 11a from the top of the discharge chamber 14. And is discharged into the condenser.

  The refrigerating machine oil R stored in the bottom of the discharge chamber 14 is fed through the oil passage 38a formed in the rear side block 30 and the salai grooves 35 and 36, which are recesses for supplying back pressure, by the high-pressure atmosphere in the discharge chamber 14, and the rear side. These are oil passages 38 a and 38 b formed in the block 30, an oil passage 44 formed in the cylinder 40, an oil passage 24 formed in the front side block 20, and a back pressure supply recess formed in the front side block 20. It is supplied to the vane groove 59 of the rotor 50 through the Sarai grooves 21 and 22, respectively, and becomes a back pressure that causes the vane 58 to protrude outward.

  The refrigerating machine oil oozes out from the gap between the vane 58 and the vane groove 59, the gap between the rotor 50 and each side block 20, 30, and the like. And also a lubricating and cooling function at the contact portion between the vane 58 and the contact portion between the vane 58 and the cylinder 40 or each of the side blocks 20 and 30, and a part of the refrigerating machine oil is used as a refrigerant in the compression chamber 43. In order to mix with gas, the oil separator 70 separates the refrigerating machine oil.

  Of the two Sarai grooves 35, 36 formed in the rear side block 30, a portion downstream of the rotor 50 in the rotational direction with respect to the proximity portion 48 of the cylinder chamber 42 (a portion corresponding to the suction stroke and the compression stroke) is formed. The refrigerating machine oil supplied to the Sarai groove 35 is supplied to the Saray groove 35 from the oil passage 38 a through a narrow gap between the bearing 37 and the outer peripheral surface of the rotary shaft 51. For this reason, the medium pressure (suction chamber) lower than the high pressure (pressure close to the discharge pressure) that is the atmosphere of the discharge chamber 14 due to the pressure loss when passing through the narrow gap between the bearing 37 and the outer peripheral surface of the rotary shaft 51. 13 is a pressure higher than the suction pressure).

  Of the two salai grooves 21 and 22 formed in the front side block 20, the refrigerating machine oil supplied to the salai groove 21 formed in the downstream portion in the rotation direction of the rotor 50 with respect to the proximity portion 48 of the cylinder chamber 42. As for the refrigeration oil supplied to the salai groove 35, the pressure becomes medium pressure.

  On the other hand, of the two salai grooves 35, 36, supply to the salai groove 36 formed in the upstream portion (mainly corresponding to the discharge stroke) of the rotor 50 with respect to the proximity portion 48 of the cylinder chamber 42. Since the refrigerating machine oil to be supplied is supplied from the oil passage 38a without pressure loss, it becomes a pressure close to the high pressure (pressure higher than the medium pressure) that is the atmosphere of the discharge chamber 14.

  Of the two salai grooves 21, 22, the salai groove 36 is also used for the refrigerating machine oil supplied to the salai groove 22 formed in the upstream portion of the rotor 50 in the rotation direction with respect to the proximity portion 48 of the cylinder chamber 42. As with the refrigerating machine oil supplied to the tank, the pressure becomes high.

  When the vane groove 59 penetrating to both end faces of the rotor 50 is connected to the Saray grooves 21, 22, 35, 36 of the side blocks 20, 30 by the rotation of the rotor 50, the connected Saray grooves 21. , 22, 35, 36 is supplied with refrigeration oil to the vane groove 59, and the pressure of the supplied refrigeration oil becomes a back pressure that causes the vane 58 to protrude.

(Detailed configuration of the first and second discharge holes 31a and 31b)
Next, the first and second discharge holes 31a and 31b formed in the rear side block 30 will be described in detail.

  First, the first discharge hole 31a formed on the upstream side immediately before the proximity portion 48 along the rotation direction W of the rotor 50 allows only one cycle of suction, compression, and discharge during one rotation of the rotor 50. This corresponds to the original single discharge hole in the gas compressor having a configuration including only a single discharge hole, and can be called a main discharge hole. On the other hand, the second discharge hole 31b formed so as to be positioned upstream of the first discharge hole 31a along the rotation direction W of the rotor 50 can be referred to as a sub discharge hole.

  As the rotor 50 rotates, the pressure of the refrigerant gas in the compression chamber 43a (see FIG. 2) facing the first discharge hole 31a becomes a high pressure that is equal to or higher than a predetermined pressure (predetermined discharge pressure). The refrigerant gas is configured to be discharged from the first discharge hole 31a. The high-pressure refrigerant gas discharged from the first discharge hole 31a is introduced into the discharge chamber 14 through the oil separator 70 via a discharge path (not shown).

  On the upstream side of the rotation direction of the rotor 50 with respect to the compression chamber 43a, the compression chamber 43b (see FIG. 2) adjacent to the compression chamber 43a is compressed when the compression chamber 43a faces the first discharge hole 31a. Although the volume of the chamber 43a is larger, the pressure of the refrigerant gas compressed in the compression chamber 43b before the compression chamber 43b rotates to the position facing the first discharge hole 31a is the predetermined pressure (predetermined discharge). Pressure) may also occur.

  In such a case, in the gas compressor in which only one discharge hole (only the first discharge hole 31a) is formed, the volume of the compression chamber 43b is further reduced with the rotation of the rotor 50, so that the compression chamber The pressure of the refrigerant gas in 43b exceeds a predetermined pressure (predetermined discharge pressure), but exceeded the predetermined pressure (predetermined discharge pressure) before the compression chamber 43b rotates to the position facing the first discharge hole 31a. The refrigerant gas is not discharged.

  For this reason, of the two vanes partitioning the compression chamber 43b (the vanes 58a and 58b in FIG. 2), the back pressure from the vane groove 59 by the refrigerating machine oil of the vane 58b on the upstream side in the rotation direction and the vane 58b When the force of pushing back the vane 58b from the cylinder 40 on the tip side due to the internal pressure of the compression chambers 43a and 43b exceeds the pushing force on the cylinder 40 due to the resultant centrifugal force, the protruding tip of the vane 58b Causes chattering that momentarily leaves the inner peripheral surface 40a of the cylinder 40.

  On the other hand, the compressor 100 of the present embodiment described above is when the pressure of the refrigerant gas in the compression chamber 43b reaches a predetermined pressure (predetermined discharge pressure) at a stage before it faces the first discharge hole 31a. The second discharge hole 31b for discharging the high-pressure refrigerant gas in the compression chamber 43b is provided on the upstream side in the rotation direction of the rotor 50 of the first discharge hole 31a.

  For this reason, even if the pressure of the refrigerant gas in the compression chamber 43b reaches a predetermined pressure (predetermined discharge pressure) before reaching the first discharge hole 31a, the refrigerant in the compression chamber 43b The gas is introduced into the discharge chamber 14 from the second discharge hole 31b through the oil separation unit 70 via a discharge path (not shown). At this time, the discharge valve 32 is elastically deformed by the high-pressure refrigerant gas discharged from the second discharge hole 31b and opened.

  Thus, the refrigerant gas in the compression chamber 43b is formed in the rear side block 30 by forming the two first discharge holes 31a and the second discharge holes 31b along the circumferential direction of the inner peripheral surface 40a of the cylinder 40. Even when the pressure reaches a predetermined pressure (predetermined discharge pressure) before reaching the first discharge hole 31a, the refrigerant gas in the compression chamber 43b is discharged from the second discharge hole 31b. Therefore, it is possible to prevent overcompression in which the pressure of the refrigerant gas in the compression chamber 43b exceeds a predetermined pressure (predetermined discharge pressure).

  Thereby, the occurrence of chattering by one vane (in FIG. 2, the vane 58a) partitioning the compression chamber 43b can be prevented. Furthermore, the power loss of the compressor 100 can be reduced and the reduction in efficiency can be suppressed.

  Further, in the compressor 100 of the present embodiment described above, the first and second discharge holes 31a and 31b are formed in the rear side block 30, so that the discharge holes formed in the radial direction from the inner peripheral surface of the cylinder as in the prior art. In addition, it is not necessary to cut out and form the discharge chamber communicating with the discharge hole. Thereby, the thickness of the entire cylinder can be sufficiently secured without increasing the outer diameter of the cylinder, so that the rigidity of the cylinder can be increased.

  In addition, since it is not necessary to provide a discharge valve and a valve support on the first discharge hole 31a side, the number of parts can be reduced.

DESCRIPTION OF SYMBOLS 10 Housing 13 Suction chamber 14 Discharge chamber 20 Front side block 30 Rear side block 31a 1st discharge hole 31b 2nd discharge hole 32 Discharge valve 33 Valve support 40 Cylinder 42 Cylinder chamber 43, 43a, 43b Compression chamber 50 Rotor 51 Rotating shaft 58 Vane 60 Compressor Body 70 Oil Separator 90 Motor 100 Compressor (Gas Compressor)

Claims (4)

A substantially cylindrical rotor that rotates integrally with the rotating shaft;
A cylinder having an inner peripheral surface with a contour shape surrounding the rotor from the outside of the outer peripheral surface of the rotor;
A plurality of plate-like vanes provided in a vane groove formed in the rotor so as to protrude from the outer peripheral surface of the rotor toward the inner peripheral surface of the cylinder;
Two side blocks respectively closing both ends of the rotor and the cylinder,
The vane forms a plurality of compression chambers by partitioning a space formed between an inner peripheral surface of the cylinder and an outer peripheral surface of the rotor, and each of the formed compression chambers is formed in the rotor. A gas compressor in which the contour shape of the inner peripheral surface of the cylinder is set so that the medium is sucked, compressed, and discharged in only one cycle during one rotation period,
The rotation of the rotor with respect to a region where the inner circumferential surface of the cylinder and the outer circumferential surface of the rotor are closest to each other in a range of one circumference around the axis of the rotation axis along the circumferential direction of the inner circumferential surface of the cylinder. On the upstream side in the direction, it has at least two discharge holes for discharging the medium compressed in the compression chamber to the outside,
The closest region is an area where the inner peripheral surface of the cylinder and the outer peripheral surface of the rotor are farthest from each other in a range of one rotation around the axis of the rotation shaft, and a position facing the rotation center of the rotor. The contour shape of the inner peripheral surface of the cylinder is set so as to be biased to the downstream side in the rotation direction of the rotor,
Of the discharge holes, at least the first discharge hole located on the side closest to the closest region is formed in one of the side blocks ,
The gas compressor is characterized in that the first discharge hole is formed so as to straddle the end surface of the cylinder and the end surface of the rotor .   2. The gas compression according to claim 1, wherein a second discharge hole is formed in one of the side blocks so as to be positioned upstream of the first discharge hole in the rotation direction of the rotor. Machine. Only around the second discharge hole, and a discharge valve for opening and closing the said discharge Deana by elastic deformation, that the valve support to prevent the warping excessively said discharge valve in medium ejected are provided The gas compressor according to claim 2 , wherein   The medium compressed in the compression chamber is discharged into a discharge chamber formed on the outer surface side of the side block through the first and second discharge holes formed in one of the side blocks. The gas compressor according to claim 3.