JP2014218985A - Gas compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a gas compressor capable of preventing excessive compression in the interior of a compression chamber and preventing unnecessary opening/closing of an on-off valve in a discharge portion.SOLUTION: A gas compressor comprises a compressor main body 60 formed such that a compression chamber 43 partitioned by a rotor 50, a cylinder 40, both side blocks 20 and 30, and vanes 58 performs only one cycle of intake, compression, and discharge in a period of one rotation of the rotor 50. In the cylinder 40, a second discharge portion 46 (another discharge portion without an on-off valve) is formed for discharging refrigerant gas G when an internal pressure of the compression chamber 43 reaches a discharge pressure before the compression chamber 43 faces a first discharge portion 45, and a third discharge portion 47 having a discharge valve 47c (an on-off valve) is formed upstream in a rotational direction W of the second discharge portion 46 at a position at which the third discharge portion 47 does not communicate with a discharge hole 46b of the second discharge portion 46 via the compression chamber 43.

Description

  The present invention relates to a gas compressor, and in particular, to an improvement in a discharge unit that discharges gas from a compression chamber.

In the air conditioning system, a gas compressor for compressing a gas such as a refrigerant gas and circulating the gas in the air conditioning system (air conditioning system) is used.
This gas compressor sucks gas into the compression chamber as the rotary shaft rotates, compresses the gas to a high pressure in the compression chamber, and discharges the compressed gas from the compression chamber through the discharge unit, thereby generating a high-pressure gas. (Patent Document 1).

JP 54-28008 A

By the way, in the compressor main body of the gas compressor described in the prior art document, each compression chamber performs gas suction, compression, and discharge from the discharge portion formed in the cylinder for only one cycle during one rotation of the rotor. Since the compression period is long, the pressure of the gas trapped inside the compression chamber reaches a predetermined discharge pressure before the compression chamber reaches the discharge section, and the inside of the compression chamber There is a risk of overcompression.
The present invention has been made in view of the above circumstances, and provides a gas compressor capable of preventing over-compression of gas inside a compression chamber and preventing unnecessary opening and closing of an on-off valve in a discharge portion. For the purpose.

  The gas compressor according to the present invention is located on the upstream side of the discharge portion without the on-off valve, and at another position not communicating with the discharge portion without the on-off valve via the compression chamber. By preventing the overcompressed state of the compression chamber, the open / close valve of the other discharge unit is prevented from being unnecessarily opened / closed by the gas flowing back into the compression chamber through the discharge unit without the open / close valve. is there.

  That is, in the gas compressor according to the present invention, the gas sucked into the compression chamber, the compression of the gas in the compression chamber, and the gas from the compression chamber through the first discharge unit during one rotation of the rotation shaft. One or more for discharging the gas in the compression chamber to the upstream side in the rotation direction of the rotary shaft with respect to the first discharge unit. Other discharge parts are formed, and among the one or more other discharge parts, the other discharge parts excluding the discharge part formed on the most upstream side in the rotation direction and the first discharge part are: Regardless of the pressure of the gas in the compression chamber, the gas in the compression chamber is discharged, and the discharge portion formed on the most upstream side is closest to the discharge portion formed on the most upstream side. To the discharge part formed on the downstream side of the It is formed at a position that does not communicate, and has an on-off valve that opens when the pressure of the gas in the compression chamber reaches a predetermined discharge pressure and does not open before reaching the predetermined discharge pressure. To do.

  According to the gas compressor of the present invention, it is possible to prevent over-compression inside the compression chamber and to prevent unnecessary opening and closing of the on-off valve in the discharge unit.

It is a longitudinal section of a vane rotary compressor which is one embodiment of a gas compressor concerning the present invention. It is sectional drawing along the AA line of the compressor part of the vane rotary compressor shown in FIG. It is a figure which shows the compressor of other embodiment, (a) is sectional drawing equivalent to FIG. 2, (b) shows the figure which shows the outer surface side of a rear side block, respectively.

  Hereinafter, specific embodiments of a gas compressor according to the present invention will be described in detail with reference to the drawings.

A vane rotary compressor 100 (hereinafter simply referred to as a compressor 100), which is an embodiment of a gas compressor according to the present invention, is an air having an evaporator, a gas compressor, a condenser, and an expansion valve installed in an automobile or the like. Used as a gas compressor in harmony systems.
This air conditioning system constitutes a refrigeration cycle by circulating a refrigerant gas G (gas).
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 portion of the cylindrical shape is closed, and the other end portion is opened.
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 12 a through which the low-pressure refrigerant gas G is introduced from the evaporator of the air conditioning system into the housing 10 through the inside and the outside of the housing 10.
On the other hand, the main body case 11 is formed with a discharge port 11a through which the high-pressure refrigerant gas G is discharged from the inside of the housing 10 to the condenser of the air conditioning system through the inside and the outside of the housing 10.

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 excites the electromagnet of the stator 90b with the electric power supplied via the power connector 90c attached to the front cover 12, thereby rotating the rotor 90a and the rotating shaft 51 around the axis C thereof. .
Although an inverter circuit 90d is provided between the power supply connector 90c and the stator 90b, a configuration in which the inverter circuit 90d is not provided may be employed.

  Although the compressor 100 of this 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 type. If the compressor 100 is of a mechanical type, instead of providing the motor 90, the rotating shaft 51 protrudes from the front cover 12 to the outside, and the leading end of the protruding rotating shaft 51 extends from the vehicle engine or the like. What is necessary is just to set it as the structure provided with the pulley, gearwheel, etc. which receive motive power transmission.

  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 fixed to the main body case 11 by a fastening member 15 such as a bolt. Has been.

The compressor main body 60 accommodated in the housing 10 includes a rotating shaft 51 that can be rotated around an axis C by a motor 90, a substantially columnar rotor 50 that rotates integrally with the rotating shaft 51, and the rotor 50. The cylinder 40 having a contour-shaped inner peripheral surface 41 that surrounds the outer peripheral surface 52 from the outside, and three sheets provided so as to protrude from the outer peripheral surface 52 of the rotor 50 toward the inner peripheral surface 41 of the cylinder 40. A plate-like vane 58 and two side blocks (front side block 20 and rear side block 30) that block both ends of the rotor 50 and the cylinder 40 are provided.
Here, 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.
Further, the compressor main body 60 partitions the space inside the housing 10 into a left space and a right space sandwiching the compressor main body 60 in FIG.

Of the two spaces partitioned inside the housing 10, the space on the left side with respect to the compressor body 60 is a low-pressure atmosphere suction chamber 13 into which low-pressure refrigerant gas G is introduced from the evaporator through the suction port 12a. The space on the right side of the compressor body 60 is a discharge chamber 14 having a high-pressure atmosphere in which high-pressure refrigerant gas G is discharged to the condenser through the discharge port 11a.
The motor 90 is disposed in the suction chamber 13.

As shown in FIG. 2, the compressor main body 60 has a substantially C-shaped single body surrounded by an inner peripheral surface 41 of the cylinder 40, an outer peripheral surface 52 of the rotor 50, and both side blocks 20 and 30. A cylinder chamber 42 is formed.
Specifically, the inner peripheral surface 41 of the cylinder 40 and the outer peripheral surface 52 of the rotor 50 are close to each other in one range (angle 360 [degrees]) around the axis C of the rotating shaft 51. The contour shape of the inner peripheral surface 41 of the cylinder 40 is set, whereby the cylinder chamber 42 forms a single space.
The proximity portion 48 formed as a portion where the inner peripheral surface 41 of the cylinder 40 and the outer peripheral surface 52 of the rotor 50 are closest to each other in the contour shape of the inner peripheral surface 41 of the cylinder 40 is the inner peripheral surface 41 of the cylinder 40. And the outer peripheral surface 52 of the rotor 50 from the remote part 49 formed as the farthest part, along the rotational direction W of the rotor 50 (clockwise direction in FIG. 2), the angle is 270 degrees or more (360). Less than [degree]) is formed at a distant position.
The contour shape of the inner peripheral surface 41 of the cylinder 40 is such that the outer peripheral surface 52 of the rotor 50 and the inner peripheral surface 41 of the cylinder 40 extend from the remote portion 49 to the proximity portion 48 along the rotation direction 51 of the rotating shaft 51 and the rotor 50. The shape is set such that the distance between and gradually decreases.

The vane 58 is accommodated in a vane groove 59 formed in the rotor 50, and protrudes outward from the outer peripheral surface 52 of the rotor 50 due to the back pressure caused by the refrigerating machine oil R and the refrigerant gas G supplied to the vane groove 59.
The vane 58 partitions 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 rotating shaft 51 and the rotor 50. It is formed.
Therefore, in the present embodiment in which the three vanes 58 are installed around the rotation shaft 51 at equal angular intervals of 120 [degrees], three to four compression chambers 43 are formed.

  In addition, in the compression chamber 43 in which the proximity portion 48 exists between the two vanes 58 and 58, the proximity portion 48 and the one vane 58 constitute one closed space, so that the two vanes 58 are provided. , 58, the compression chamber 43 positioned with the proximity portion 48 sandwiched therebetween is divided into two spaces, so that four compression chambers 43 are formed even for three vanes.

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

  A portion of the cylinder chamber 42 on the most upstream side in the rotation direction W (a portion on the downstream side of the proximity portion 48 along the rotation direction W) leads to the suction chamber 13 formed in the front side block 20. Suction hole 23 (In FIG. 2, the front side block 20 is located on the front side of the drawing with respect to the cross section, and therefore, the suction hole 23 formed in the front side block 20 is indicated by a two-dot chain imaginary line.) Is facing.

On the other hand, a first discharge formed in the cylinder 40 is formed in a portion of the cylinder chamber 42 on the most downstream side in the rotation direction W of the rotor 50 (a portion on the upstream side with respect to the proximity portion 48 along the rotation direction W). A discharge hole 45b that communicates with the discharge chamber 45a of the section 45 faces, and on the upstream side, a discharge hole 46b that communicates with the discharge chamber 46a of the second discharge section 46 (other discharge section) formed in the cylinder 40. I'm here.
The discharge hole 46b of the second discharge part 46 is formed at an angular position within an angle of 90 [degrees] around the axis C and upstream of the rotation direction W with respect to the discharge hole 45b of the first discharge part 45. In addition, the two discharge holes 45b and 46b are arranged so that the two discharge holes 45b and 46b can communicate with each other through one compression chamber 43 in a discharge stroke described later.

Further, on the upstream side of the cylinder chamber 42 in the rotation direction W from the second discharge portion 46, a third discharge portion 47 formed in the cylinder 40 (the most upstream side in the rotation direction W among the other discharge portions). A discharge hole 47b communicating with the discharge chamber 47a of the discharge portion formed at the top is facing.
When the pressure of the refrigerant gas G in the compression chamber 43 facing the discharge hole 47b is equal to or higher than the pressure (discharge pressure) in the discharge chamber 47a, the third discharge portion 47 warps toward the discharge chamber 47a due to the differential pressure. And a discharge valve 47c (open / close valve) that closes the discharge hole 47b by elastic force when the pressure of the refrigerant gas G is less than the pressure (discharge pressure) in the discharge chamber 47a. 47c is provided with a valve support 47d that prevents excessive elastic deformation of 47c on the discharge chamber 47a side.

The discharge hole 47b of the third discharge part 47 is formed at an angular position that exceeds the angle 120 [degrees] upstream of the rotation direction W around the axis C with respect to the discharge hole 46b of the second discharge part 46. In addition, the two discharge holes 46b and 47b are arranged so that the two discharge holes 46b and 47b do not communicate with each other through one compression chamber 43 in a discharge stroke described later.
Note that the second discharge unit 46 is a discharge unit formed on the downstream side closest to the third discharge unit 47 in the rotation direction W.

  The contour shape of the inner peripheral surface 41 of the cylinder 40 is that the refrigerant gas G is sucked into the compression chamber 43 from the suction chamber 13 through the suction hole formed in the front side block 20, and the refrigerant gas G is compressed in the compression chamber 43. The discharge of the refrigerant gas G from the compression chamber 43 to the discharge chamber 45a through the discharge hole 45b of the first discharge portion 45 is set to be performed for one cycle during one rotation of the rotor 50.

On the most upstream side in the rotation direction W of the rotor 50, the contour shape of the inner peripheral surface 41 is set so that the distance between the inner peripheral surface 41 of the cylinder 40 and the outer peripheral surface 52 of the rotor 50 increases rapidly from a small state. In the angular range including the remote portion 49, the vane 58 on the downstream side (front side) in the rotation direction W of the two vanes 58 and 58 partitioning the compression chamber 43 is inhaled by the rotation in the rotation direction W. After passing through 23, a stroke (suction stroke) is performed in which the refrigerant gas G is sucked into the compression chamber 43 through the suction hole 23 formed in the front side block 20 due to the expansion of the volume of the compression chamber 43.
Next, after the vane 58 on the upstream side (rear side) in the rotation direction W of the two vanes 58 and 58 partitioning the compression chamber 43 passes through the suction hole 23, the refrigerant gas G is confined in the compression chamber 43. The contour shape of the inner peripheral surface 41 of the cylinder 40 is set so that the distance between the inner peripheral surface 41 and the outer peripheral surface 52 of the rotor 50 gradually decreases toward the downstream in the rotational direction W. As the rotor 50 rotates, the volume of the compression chamber 43 decreases, and a stroke (compression stroke) in which the refrigerant gas G in the compression chamber 43 is compressed.
Further, on the downstream side in the rotation direction W of the rotor 50, the interval between the inner peripheral surface 41 of the cylinder 40 and the outer peripheral surface 52 of the rotor 50 is further reduced, and the compression of the refrigerant gas G further proceeds. When the rotation angle position facing 46b or the discharge hole 46b is reached, the refrigerant gas G in the compression chamber 43 is discharged into the discharge chambers 45a and 46a (discharge process) through the discharge holes 46b and 45b.

  As the rotor 50 rotates, each compression chamber 43 repeats the suction stroke, the compression stroke, and the discharge stroke in this order, so that the low-pressure refrigerant gas G sucked from the suction chamber 13 becomes high pressure and the compressor It is discharged to a cyclone block 70 (oil separator) that is outside the main body 60.

The first discharge unit 45 and the second discharge unit 46 do not include an opening / closing valve like the discharge valve 47c in the third discharge unit 47, and the discharge holes 45b and 46b and the discharge chambers 45a and 46a. Are provided so that the refrigerant gas G inside the compression chamber 43 is discharged regardless of the pressure of the refrigerant gas G inside the compression chamber 43 facing the discharge holes 45b and 46b. It has become.
That is, the first discharge unit 45 and the second discharge unit 46 discharge the refrigerant gas G in the compression chamber 43 when the volume of the compression chamber 43 reaches a predetermined compression ratio. The discharge section 47 discharges the refrigerant gas G in the compression chamber 43 only when the above-described differential pressure exceeds a predetermined value, and before the differential pressure reaches the predetermined value, The refrigerant gas G is not discharged.

The discharge chamber 45a of the first discharge unit 45 faces a discharge passage 38 formed so as to penetrate to the outer surface of the rear side block 30 (the surface facing the discharge chamber 14). The discharge chamber 45a passes through the discharge passage 38. To the cyclone block 70 attached to the outer surface of the rear side block 30.
The discharge chamber 46a of the second discharge unit 46 also faces a discharge passage 39a formed so as to penetrate to the outer surface of the rear side block 30 (the surface facing the discharge chamber 14). The discharge chamber 46a passes through the discharge passage 39a. To the cyclone block 70 attached to the outer surface of the rear side block 30.
Therefore, the refrigerant gas G discharged to the discharge chamber 45a of the first discharge portion 45 is discharged to the cyclone block 70 through the discharge passage 38 and discharged to the discharge chamber 46a of the second discharge portion 46. G is discharged to the cyclone block 70 through the discharge passage 39a.

On the other hand, the discharge chamber 47a of the third discharge portion 47 also faces the discharge passage 39b formed so as to penetrate to the outer surface of the rear side block 30 (the surface facing the discharge chamber 14). The discharge passage 39a.
Therefore, the refrigerant gas G discharged to the discharge chamber 47a of the third discharge portion 47 is discharged from the discharge passage 39b to the cyclone block 70 via the discharge passage 39a.

The cyclone block 70 is attached to the outer surface of the rear side block 30 on the downstream side of the flow of the refrigerant gas G with respect to the compressor main body 60, and supplies the refrigerating machine oil R mixed with the refrigerant gas G discharged from the compressor main body 60. It is separated from the refrigerant gas G.
Specifically, the refrigerant gas G discharged from the discharge hole 45 b of the first discharge portion 45 to the discharge chamber 45 a and discharged from the compressor main body 60 through the discharge passage 38, the discharge hole 46 b of the second discharge portion 46. The refrigerant gas G discharged from the discharge chamber 46a through the discharge passage 39a and discharged from the compressor main body 60, and the discharge valve 47c from the discharge hole 47b of the third discharge portion 47 are opened and discharged to the discharge chamber 46a. The refrigerating machine oil R is centrifuged from the refrigerant gas G by rotating the refrigerant gas G discharged from the compressor main body 60 through the passages 39b and 39a in a spiral.

  The refrigerating machine oil R separated from the refrigerant gas G is accumulated at the bottom of the discharge chamber 14, and the high-pressure refrigerant gas G after the refrigerating machine oil R is separated is discharged into the discharge chamber 14 and then condensed through the discharge port 11a. Discharged into the container.

The refrigerating machine oil R stored at the bottom of the discharge chamber 14 is supplied with oil passages 34a formed in the rear side block 30 and salai grooves that are back pressure supply recesses formed in the rear side block 30 due to the high pressure atmosphere in the discharge chamber 14. 31, 32, and oil passages 34 a and 34 b formed in the rear side block 30, an oil passage 44 formed in the cylinder 40, an oil passage 24 formed in the front side block 20, and the front side block 20. It is supplied to the vane groove 59 through the Sarai grooves 21 and 22 which are recesses for supplying back pressure.
That is, when the vane groove 59 penetrating to both end faces of the rotor 50 is connected to the Sarai grooves 21 and 31 or the Saray grooves 22 and 32 of the side blocks 20 and 30 by the rotation of the rotor 50, the connected salai grooves The refrigerating machine oil R is supplied to the vane groove 59 from the grooves 21, 31 or the Sarai grooves 22, 32, and the pressure of the supplied refrigerating machine oil R becomes a back pressure that causes the vane 58 to protrude outward.

Here, the passage through which the refrigerating machine oil R passes between the oil passage 34 a of the rear side block 30 and the Sarai groove 31 is between the bearing 37 of the rear side block 30 and the outer peripheral surface of the rotary shaft 51 supported by the bearing 37. It is a very narrow gap.
The refrigerating machine oil R has the same high pressure as the high-pressure atmosphere in the discharge chamber 14 in the oil passage 34 a, but receives pressure loss while passing through this narrow gap, and when it reaches the Saray groove 31, The intermediate pressure is lower than the pressure.
Here, the intermediate pressure is a pressure that is higher than the low pressure that is the pressure of the refrigerant gas G in the suction chamber 13 and lower than the high pressure that is the pressure of the refrigerant gas G in the discharge chamber 14.

Similarly, the passage through which the refrigerating machine oil R passes between the oil passage 24 of the front side block 20 and the Sarai groove 21 is the bearing 27 of the front side block 20 and the outer peripheral surface of the rotary shaft 51 supported by the bearing 27. It is a very narrow gap between.
The refrigerating machine oil R has the same high pressure as the high pressure atmosphere of the discharge chamber 14 in the oil passage 24, but receives a pressure loss while passing through this narrow gap, and when it reaches the Saray groove 21, The intermediate pressure is lower than the internal pressure.
Therefore, the back pressure that is supplied from the Sarai grooves 21 and 31 to the vane groove 59 and causes the vane 58 to protrude toward the inner peripheral surface 41 of the cylinder 40 is an intermediate pressure of the refrigerator oil R.

  On the other hand, the Saray grooves 22 and 32 are formed so as to communicate with the oil passages 24 and 34 without pressure loss, and the Saray grooves 22 and 32 have a high pressure which is a high pressure equivalent to the pressure inside the discharge chamber 14. In the final stage of the compression stroke in which the refrigerating machine oil R is supplied and the vane groove 59 communicates with the saray grooves 22 and 32, the refrigerant gas in the compression chamber 43 in the final stage of the compression stroke is supplied by supplying a high pressure back pressure to the vane 58. The high pressure of G can be counteracted and chattering of the vane 58 is prevented.

  The refrigerating machine oil R starts to ooze out from the gap between the vane 58 and the vane groove 59, the gap between the rotor 50 and the side blocks 20, 30, and the like, and is formed between the rotor 50 and the side blocks 20, 30. A lubricating portion and a cooling function are also exerted in a contact portion between them and a contact portion between the vane 58 and the cylinder 40 or both side blocks 20 and 30, and a part of the refrigerating machine oil R is used as a refrigerant in the compression chamber 43. In order to be mixed with the gas G, the refrigerating machine oil R is separated by the cyclone block 70.

  According to the compressor 100 of the present embodiment configured as described above, each compression chamber 43 causes the low-pressure refrigerant gas G in the suction chamber 13 to pass through the suction hole 23 in the suction stroke as the rotary shaft 51 rotates. The refrigerant gas G sucked is compressed in the compression stroke, and the refrigerant gas G compressed to a high pressure is discharged to the discharge chambers 45a and 46a through the discharge holes 46b and 45b in the discharge stroke.

Here, the compression ratio of the compression chamber 43 in the compressor main body 60 is always constant because it is defined by the volume ratio of the compression chamber 43, but the air conditioner includes the compressor 100, the evaporator, the condenser, and the expansion valve. The compression ratio in the operating state of the system varies depending on the operating condition of the air conditioning system and the load such as the environmental temperature.
For this reason, when the compression ratio in the operating state of the air conditioning system is equal to or less than the compression ratio of the compressor body 60, the compression chamber 43 is in a stage before the compression chamber 43 faces the discharge hole 46b of the second discharge portion 46. The pressure of the refrigerant gas G inside reaches the discharge pressure of the refrigerant gas G assumed by the compression ratio of the compressor body 60, and the inside of the compression chamber 43 may be overcompressed.

  However, in the compressor 100 of the present embodiment, the third discharge portion 47 is provided on the upstream side in the rotation direction W from the discharge hole 46b of the second discharge portion 46, and the compression chamber 43 is the third discharge portion. When the pressure of the refrigerant gas G inside the compression chamber 43 reaches the discharge pressure of the refrigerant gas G assumed by the compression ratio of the compressor body 60 at a stage before facing the 47 discharge holes 47b, the compression chamber During a period in which 43 is facing the discharge hole 47b of the third discharge part 47, the discharge valve 47c of the third discharge part 47 is opened, and the refrigerant gas G inside the compression chamber 43 is discharged into the discharge chamber through the discharge hole 47b. Since it discharges to 47a, it can prevent that the inside of the compression chamber 43 will be in an overcompressed state.

Further, when the compression ratio in the operating state of the air conditioning system is equal to or higher than the compression ratio of the compressor body 60, the compression chamber 43 has the discharge holes 45b of the first discharge unit 45 and the discharge holes 46b of the second discharge unit 46. , The refrigerant gas G may flow back into the compression chamber 43 from the discharge chamber 14 through the discharge chambers 45a and 46a.
Here, it is assumed that the discharge hole 47 b of the third discharge part 47 is formed at a position communicating with the discharge hole 45 b of the first discharge part 45 and the discharge hole 46 b of the second discharge part 46 via the compression chamber 43. Assuming that the discharge chamber 45a and the discharge hole 45b of the first discharge part 45 and the discharge chamber 46a and the discharge hole 46b of the second discharge part 46 are compressed by the refrigerant gas G flowing into the compression chamber 43 The discharge valve 47c opens despite the pressure inside the chamber 43 becoming high and it is not necessary to open it. When the vane 58 on the upstream side in the rotation direction W of the compression chamber 43 passes through the discharge hole 47b, the discharge valve 47c close up.
When the discharge valve 47c is opened, a sound is generated when the discharge valve 47c hits the valve support 47d. When the discharge valve 47c is closed, a sound is generated when the discharge valve 47c hits a wall surface at the time of the discharge hole 47b.

When the refrigerant gas G flows into the compression chamber 43 from the discharge chamber 45a of the first discharge section 45 or the discharge chamber 46a of the second discharge section 46, the compression chamber 43 discharges from the first discharge section 45. Since it communicates with the chamber 45a or the discharge chamber 46a of the second discharge portion 46, the discharge valve 47c of the third discharge portion 47 does not need to be opened as described above.
As described above, the discharge hole 47 b of the third discharge unit 47 is temporarily connected to the discharge hole 45 b of the first discharge unit 45 and the discharge hole 46 b of the second discharge unit 46 through the compression chamber 43. If it is formed, useless sound may be generated by the discharge valve 47c of the third discharge portion 47.

  However, in the compressor 100 of the present embodiment, the discharge hole 47b of the third discharge part 47 is connected to the discharge hole 45b of the first discharge part 45 and the discharge hole 46b of the second discharge part 46 via the compression chamber 43. Even if there is a backflow of the refrigerant gas G to the compression chamber 43 via the discharge hole 45b of the first discharge part 45 or the discharge hole 46b of the second discharge part 46 because it is formed at a position that does not communicate. Since the compression chamber 43 in which the backflow of the refrigerant gas G has occurred does not face the discharge hole 47b of the third discharge portion 47, the discharge valve 47c can be unnecessarily opened and closed by the refrigerant gas G flowing back into the compression chamber 43. In addition, it is possible to prevent the generation of sound due to the opening and closing of the discharge valve 47c.

  The compressor 100 of the present embodiment is obtained by joining the discharge passage 39b of the third discharge portion 47 having the discharge valve 47c as an on-off valve to the discharge passage 39a of the second discharge portion 46. The gas compressor according to the present invention is not limited to this form, and the discharge passage 39b may be formed so as to communicate directly with the cyclone block 70 independently of the discharge passage 38 and the discharge passage 39a. .

In the compressor 100 of the present embodiment, the third discharge unit 47 is formed in the cylinder 40 in the same manner as the first discharge unit 45 and the second discharge unit 46 without the on-off valve. The gas compressor according to the invention is not limited to this form, and the third discharge portion 47 described above may be formed in the rear side block 30 as shown in FIG. 3, for example.
That is, the discharge hole 47b of the third discharge part 47 is formed in the discharge hole 46b of the second discharge part 46 in the inner surface 30a of the rear side block 30 facing the compression chamber 43, as shown in FIG. On the other hand, it is formed so as to penetrate the outer surface 30b of the rear side block 30 from an angular position exceeding the angle 120 [degrees] on the upstream side in the rotation direction W around the axis C, and both the discharge holes 46b and 47b are discharged. The two discharge holes 46b and 47b are arranged so as not to communicate with each other through one compression chamber 43 in the stroke.

Then, as shown in FIG. 3B, a discharge valve 47c is provided at a portion where the discharge hole 47b is opened at the outer surface 30b of the rear side block 30, and closes the discharge hole 47b.
As shown in FIG. 3B, the discharge passages 38, 39a, 39b are all exposed at the outer surface 30b of the rear side block 30, but the cyclone block 70 installed on the outer surface 30b of the rear side block 30 is By covering all of the exposed discharge passages 38, 39a and 39b, the refrigerant gas G flowing through these discharge passages 38, 39a and 39b is guided to the cyclone block 70 without leakage.

  The compressor 100 of the present embodiment has three vanes 58, but the number of vanes 58 may be two, four or more, and the third discharge The discharge holes 47 b of the portion 47 are formed at positions corresponding to the number of vanes 58 from the position of the discharge holes 46 b of the second discharge portion 46.

Specifically, when the number of the vanes 58 is two, the discharge holes 47b of the third discharge portion 47 are rotated around the axis C with respect to the rotation direction W with respect to the discharge holes 46b of the second discharge portion 46. The two discharge holes 46b and 47b are arranged so that the two discharge holes 46b and 47b do not communicate with each other through one compression chamber 43 in the discharge stroke. ing.
When the number of vanes 58 is four, the discharge holes 47b of the third discharge portion 47 are angled with respect to the discharge holes 46b of the second discharge portion 46 around the axis C and upstream in the rotational direction W. The two discharge holes 46b and 47b are formed so as not to communicate with each other through one compression chamber 43 in the discharge stroke.
When the number of vanes 58 is five, the discharge holes 47b of the third discharge portion 47 are angled with respect to the discharge holes 46b of the second discharge portion 46 around the axis C and upstream in the rotational direction W. The two discharge holes 46b and 47b are arranged so as not to communicate with each other through one compression chamber 43 in the discharge stroke.
Similarly, when the number of vanes 58 is six, the discharge hole 47b of the third discharge part 47 is upstream of the rotation direction W around the axis C with respect to the discharge hole 46b of the second discharge part 46. The two discharge holes 46b and 47b are arranged so that the two discharge holes 46b and 47b do not communicate with each other through one compression chamber 43 in the discharge stroke. .

The compressor 100 according to the present embodiment includes a second discharge unit 46 having no discharge valve (open / close valve) on the upstream side in the rotation direction W with respect to the first discharge unit 45, similarly to the first discharge unit 45. However, the gas compressor according to the present invention is not limited to this form, and may not include the second discharge portion 46.
In this case, since the first discharge unit 45 is a discharge unit formed on the downstream side closest to the third discharge unit 47 in the rotation direction W, the third discharge unit 47 including the discharge valve 47c is used. The discharge hole 47b is formed at an angular position exceeding the angle 120 [degrees] around the axis C and upstream of the rotation direction W with respect to the discharge hole 45b of the first discharge part 45. 45b and 47b should just be arrange | positioned so that both the discharge holes 45b and 47b may not mutually communicate through the one compression chamber 43 in a discharge stroke.

The discharge hole 45b of the first discharge portion 45 does not coincide with the proximity portion 48 of the cylinder 40, and is disposed upstream of the proximity portion 48 of the cylinder 40 in the rotation direction W of the rotation shaft 51. After the vane 58 on the upstream side in the rotation direction W of the compression chamber 43 passes through the discharge hole 45b of the first discharge portion 45, the compression chamber 43 is partitioned by the proximity portion 48 on the upstream side in the rotation direction W. The downstream side in the direction W is a space partitioned by the vanes 58.
If the refrigerant gas G that remains slightly in the compression chamber 43 is not discharged from the compression chamber 43, the inside of the compression chamber 43 may be overcompressed, and chattering of the downstream vane 58 may occur.
Therefore, chamfering or notching (may be a hole leading to the outside; the same shall apply hereinafter) is formed in a portion of the inner peripheral surface 41 of the cylinder 40 extending from the discharge hole 45 b to the proximity portion 48, and slightly in the compression chamber 43. By letting the remaining refrigerant gas G escape to the discharge hole 45b through this chamfering or notch, the compression chamber 43 after passing through the first discharge portion 45 can be prevented from being overcompressed.

  The compressor 100 of the present embodiment is a vane rotary type gas compressor, but the gas compressor according to the present invention is not limited to this type, and the compression chamber is formed during one rotation of the rotating shaft. Any type of gas as long as it has a compressor body formed so as to perform one cycle of gas suction into the compression chamber, gas compression in the compression chamber, and gas discharge from the compression chamber through the first discharge section It may be a compressor.

20 Front side block 30 Rear side block 40 Cylinder 42 Cylinder chamber 43 Compression chamber 45 First discharge part 46 Second discharge part (other discharge part)
47 3rd discharge part (discharge part formed in the most upstream of rotation direction among other discharge parts)
45a, 46a, 47a Discharge chamber 45b, 46b, 47b Discharge hole 47c Discharge valve 50 Rotor 51 Rotating shaft 58 Vane 60 Compressor body 100 Vane rotary compressor (gas compressor)
G Refrigerant gas (gas)
W Rotation direction

Claims (5)

During the period of one rotation of the rotary shaft, the gas is sucked into the compression chamber, the gas is compressed in the compression chamber, and the gas is discharged from the compression chamber through the first discharge portion for only one cycle. Equipped with a compressor body,
One or more other discharge portions for discharging the gas in the compression chamber are formed on the upstream side in the rotation direction of the rotation shaft with respect to the first discharge portion,
Of the one or more other discharge sections, the other discharge sections and the first discharge section excluding the discharge section formed on the most upstream side in the rotation direction are adjusted to the pressure of the gas in the compression chamber. Regardless, it discharges the gas in the compression chamber,
The discharge part formed on the most upstream side is formed at a position not communicating with the discharge part formed on the nearest downstream side with respect to the discharge part formed on the most upstream side via the compression chamber. And an open / close valve that opens when the gas pressure in the compression chamber reaches a predetermined discharge pressure and does not open before the gas reaches the predetermined discharge pressure. The other discharge parts excluding the discharge part formed on the most upstream side and the first discharge part have a discharge chamber, and a discharge hole through which the compression chamber and the discharge chamber are passed,
The discharge portion formed on the most upstream side is more than the discharge chamber in which the gas discharged through the other discharge portions excluding the discharge portion formed on the most upstream side and the first discharge portion flows. The gas compressor according to claim 1, wherein the gas compressor is connected to a discharge passage formed on the downstream side. The compressor body is formed in a substantially cylindrical rotor that rotates about the axis together with the rotary shaft, a cylinder having a contoured inner peripheral surface that surrounds the rotor from the outside of the outer peripheral surface of the rotor, and the rotor A plurality of plate-like vanes that are inserted into the formed vane grooves and project outward from the rotor, and two side blocks that are in contact with both end surfaces of the rotor and the cylinder and cover these both end surfaces. Have
3. The gas compressor according to claim 1, wherein the compression chamber is formed in a plurality of partitions partitioned by the rotor, the cylinder, the side blocks, and the vane.   The gas compressor according to claim 3, wherein the discharge portion formed on the most upstream side is formed on the cylinder.   The gas compressor according to claim 3, wherein the discharge part formed on the most upstream side is formed on the side block.