JP2013130185A - Gas compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To raise efficiency of a gas compressor.SOLUTION: A gas compressor is provided with a cylinder member 21, a rotor 22, and vanes 25. A proximity section 51 is provided between the cylinder member 21 and the rotor 22, and this forms a single cylinder chamber 27 for performing only one cycle of compression of a refrigerant gas 26 per rotation. At least one auxiliary discharge section 54 is provided upstream of a discharge section 29. When the pressure of the refrigerant gas 26 within a compression chamber 24 reaches a discharge pressure P, the auxiliary discharge section 54 releases the pressure within the compression chamber 24 and maintains the pressure at the discharge pressure P.

Description

  The present invention relates to a gas compressor capable of improving efficiency.

  A vehicle such as an automobile is provided with an air conditioner (air conditioner) for adjusting the temperature in the passenger compartment.

  This air conditioner includes a loop-shaped refrigerant cycle in which a refrigerant (cooling medium) is circulated, and an evaporator, a gas compressor, a condenser, and an expansion valve are provided in this refrigerant cycle in this order. Yes.

  The gas compressor described above compresses the gaseous refrigerant (refrigerant gas) evaporated by the evaporator into a high-temperature and high-pressure refrigerant gas and sends it to the condenser.

  There exists a vane rotary type compressor (vane rotary compressor) in such a gas compressor (for example, refer to patent documents 1).

  This vane rotary type compressor has a hollow cylinder member, a rotor rotatably disposed inside the cylinder member, and a protrusion that is slidably attached to the rotor and has a tip sliding on the inner peripheral surface of the cylinder member. A plurality of vanes capable of forming a plurality of compression chambers inside the cylinder member by being in contact with each other are provided.

  A cylinder chamber for performing a refrigerant gas compression cycle is formed between the cylinder member and the rotor by changing the volume of the compression chamber, and the refrigerant gas can be sucked into the upstream side of the cylinder chamber. A suction part is provided, and a discharge part capable of discharging the refrigerant gas is provided on the downstream side.

JP 54-28008 A

  However, the compressor has the following problems.

  That is, the vane rotary type compressor tended to have lower efficiency (coefficient of performance or COP (Coefficient Of Performance)) than other types of compressors.

  This is considered due to the following causes.

In other words, the vane rotary type compressor
1. Because the refrigerant gas is compressed rapidly, over-compression is likely to occur, and power loss increases accordingly.
2. In order to rapidly compress the refrigerant gas, the pressure difference between the adjacent compression chambers increases, and the refrigerant gas tends to leak from the vane due to the pressure difference.
That's it.

  This is particularly a problem during high-load operation. This problem does not occur only when the object to be compressed by the compressor is a refrigerant gas, but the same applies to gases in general.

  In order to solve the above-described problems, a gas compressor according to the present invention includes a hollow cylinder member, a rotor rotatably disposed inside the cylinder member, and a tip that is attached to the rotor so as to project and be retractable. And a plurality of vanes capable of forming a plurality of compression chambers inside the cylinder member by slidingly contacting the inner peripheral surface of the cylinder member, and the volume of the compression chamber is increased between the cylinder member and the rotor. A cylinder chamber for performing a compression cycle of a gas such as a refrigerant gas is formed by changing, and a suction portion capable of sucking gas is provided on the upstream side of the cylinder chamber, and a discharge portion capable of discharging gas on the downstream side. In the provided gas compressor, the gas compression cycle is performed only once per revolution for each compression chamber by providing only one close portion between the cylinder member and the rotor. A sub-cylinder is formed by forming a single cylinder chamber and maintaining the discharge pressure by releasing the pressure in the compression chamber when the pressure of the gas in the compression chamber reaches the discharge pressure upstream of the discharge unit. It is characterized in that at least one part is provided.

  In the gas compressor according to the present invention, the sub-discharge portion is installed with an interval equal to or slightly narrower than the adjacent discharge portion or the sub-discharge portion between the tips of adjacent vanes. Preferably it is.

  Alternatively, in the gas compressor according to the present invention, on the inner peripheral surface of the cylinder between the adjacent edge portions between the discharge portion and the sub-discharge portion that move back and forth along the rotation direction of the vane. The length along the inner circumferential surface of the cylinder between the adjacent edges between the two sub-ejection parts that follow each other along the rotation direction of the vane. The sub-discharge part is arranged so that the tip of two vanes that follow each other in the direction is shorter than the length along the inner peripheral surface of the cylinder between the contact points where the tips of the vanes contact the inner peripheral surface of the cylinder. It is preferable that it is installed.

  In the above-described gas compressor according to the present invention, it is preferable that the sub-discharge portion and the adjacent discharge portion or the sub-discharge portion are arranged at intervals at which gas discharge from the compression chamber is not interrupted.

  Furthermore, in the gas compressor according to the present invention, the maximum gap portion where the radial gap between the cylinder member and the rotor in the cylinder chamber is maximized is closer than the angle 90 [degrees] in the rotation direction from the proximity portion. It is preferable to set to the side position.

  According to the gas compressor concerning the present invention, the following operation effects can be obtained by the above configuration.

  That is, the gas can be gently compressed by unifying the cylinder chamber and performing the gas compression cycle only once per rotation for each compression chamber. As a result, the required power can be reduced and the differential pressure between the adjacent compression chambers can be reduced to prevent the gas from leaking from the vane and the volume efficiency from being lowered.

  Further, by providing at least one or more sub-discharge sections upstream of the discharge section, when the pressure of the gas in the compression chamber reaches the discharge pressure, the pressure in the compression chamber is extracted from the sub-discharge section to the discharge pressure. Therefore, it is possible to reliably prevent the compression chamber from being over-compressed. As a result, wasteful power consumption due to overcompression can be suppressed and efficiency can be improved.

  In the present invention, according to a preferred configuration in which the sub-ejection part is installed with an interval equal to or slightly narrower than the adjacent ejection part or the sub-ejection part between the tips of the adjacent vanes. The following effects can be obtained.

  In other words, by arranging the sub-discharge portion and the adjacent discharge portion or the sub-discharge portion at the same interval as or slightly narrower than the tip of the adjacent vane, the sub-discharge portion can be prevented from being over-compressed. It becomes possible to arrange efficiently in a required position.

  In the present invention, the distance along the inner peripheral surface of the cylinder between the adjacent edges between the discharge section and the sub-discharge section that follow each other along the rotation direction of the vane, or along the rotation direction of the vane. The distance along the inner peripheral surface of the cylinder between the adjacent edge portions between the two sub-discharge sections that are adjacent to each other is such that the tips of the two vanes that follow each other along the rotational direction According to the preferred configuration in which the sub-discharge portion is installed so as to be shorter than the distance along the inner peripheral surface of the cylinder between the contact points in contact with the peripheral surface, the following operational effects can be obtained. it can.

  That is, the compression chamber defined by two vanes that follow each other along the rotation direction faces the sub-discharge portion before the discharge portion, and the vane on the upstream side (rear side) in the rotation direction of the compression chamber Since the vane on the downstream side (front side) in the rotation direction of the compression chamber faces the discharge portion before passing the sub discharge portion, the sub discharge portion is efficiently placed at a position necessary for preventing over compression. It becomes possible to arrange.

  In the present invention, according to a preferred configuration in which the sub-ejection unit and the adjacent ejection unit or the sub-ejection unit are arranged at intervals at which gas ejection from the compression chamber is not interrupted, the following operational effects are obtained. be able to.

  That is, by arranging the sub-discharge part and the adjacent discharge part or the sub-discharge part at an interval at which the gas discharge from the compression chamber is not interrupted, the gas discharge from the compression chamber is interrupted to newly It is possible to prevent over-compression.

  In the present invention, the maximum spacing portion at which the radial spacing between the cylinder member and the rotor in the cylinder chamber is maximized is set to a position on the nearer side than the angle 90 [degrees] in the rotational direction from the proximity portion. According to the preferred configuration, the following operational effects can be obtained.

  That is, by setting the maximum gap portion where the radial gap between the cylinder member and the rotor in the cylinder chamber is maximum at a position closer to the rotation direction than the angle 90 [degrees] from the proximity portion, the suction stroke is reduced. The process can be completed at an earlier timing, thereby making it possible to advantageously perform the compression stroke and the discharge stroke and improve the efficiency.

It is sectional drawing which looked at the gas compressor concerning the Example of this invention from the side. It is sectional drawing along the AA line of the compressor part of FIG. It is a graph which shows the relationship between the pressure and rotational angle for demonstrating the effect of this Example. (A) is a schematic diagram which shows the magnitude relationship between the length between the edge of the sub-discharge part installed in the upstream of a discharge part, and the edge of a discharge part, and the length between vanes, (b) ) Is a schematic diagram showing the magnitude relationship between the length between the edges of two adjacent sub-discharge sections and the length between the vanes when two or more sub-discharge sections are provided on the upstream side of the discharge section. It is. FIG. 5 is a view corresponding to FIG. 4 showing another embodiment, and (a) is a length between the edge of the sub-discharge portion and the edge of the discharge portion installed on the upstream side of the discharge portion and between the vanes. It is a schematic diagram which shows the magnitude relationship with length, (b) is between the edge parts of the two sub-discharge parts which precede and follow when two or more sub-discharge parts are provided in the upstream of the discharge part. It is a schematic diagram which shows the magnitude relationship between the length and the length between vanes.

  DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments embodying the present invention will be described below in detail with reference to the drawings.

  1 to 5 show this embodiment and its modifications.

<Configuration> The configuration will be described below.
A vehicle such as an automobile is provided with an air conditioner (air conditioner) for adjusting the temperature in the passenger compartment.

  This air conditioner includes a loop-like refrigerant cycle in which a cooling medium (hereinafter referred to as a refrigerant) is circulated. The refrigerant cycle includes an evaporator, a gas compressor, a condenser, and an expansion valve. It is provided in order.

  The gas compressor described above compresses a gaseous refrigerant (hereinafter referred to as a refrigerant gas) as an example of the gas evaporated by the evaporator to form a high-temperature and high-pressure refrigerant gas, which is sent to the condenser. is there.

  There are various types of such gas compressors, and among them, a vane rotary type compressor (vane rotary compressor) has the following structure. The following is an example of an electric vane rotary compressor. However, it is not limited to the electric type.

  As shown in FIG. 1, the main body of the compressor 1 is mainly composed of a front cover 2 and a main body case 4. The “front cover 2” has a lid shape, and the “main body case 4” has a container shape with one end opened, so that the front cover 2 closes the opening of the main body case 4. It has become.

  Inside the compressor 1, a rotating shaft 6 is disposed at an axial center position. The rotary shaft 6 is rotatably supported by bearings 7 to 9 provided inside the main body of the compressor 1. A bearing portion 7 that pivotally supports one end of the rotary shaft 6 is provided on the front cover 2. The bearing portions 8 and 9 that pivotally support the other end of the rotating shaft 6 will be described later.

  Inside the compressor 1, a motor unit 11 and a compressor unit 12 are provided. The rotating shaft 6 described above is shared by the motor unit 11 and the compressor unit 12.

  The above-described “motor unit 11” includes a rotor 11a attached to the outer periphery of one end side of the rotating shaft 6, and a stator 11b attached to the inside of one end side of the front cover 2 so as to surround the rotor 11a. Yes. For example, the rotor 11a is a permanent magnet, and the stator 11b is an electromagnet or the like to constitute a multiphase brushless DC motor or the like. However, the configuration of the rotor 11a and the stator 11b is not limited to this. And the motor part 11 excites the electromagnet of the stator 11b with the electric power supplied from the power supply connector 11c attached to the front cover 2, and generates a rotating magnetic field between the rotor 11a and the stator 11b, thereby rotating the rotating shaft. 6 can be driven to rotate. An inverter circuit 11d and the like are provided between the power connector 11c and the stator 11b as necessary.

  In the case of the mechanical compressor 1, instead of providing the motor unit 11 described above, the rotating shaft 6 is protruded from the front cover 2 to the outside, and the engine of the vehicle is provided at the tip of the protruding rotating shaft 6. A driving belt pulley for transmitting the power from the motor to the rotating shaft 6 via a driving force transmitting means such as a belt is attached.

  On the other hand, the above-described “compressor section 12” mainly includes a compression section 15 and an oil separation section 16.

  Among these, as shown in FIG. 2, the “compressing portion 15” described above includes a hollow cylinder member 21 (cylinder block), a rotor 22 rotatably disposed inside the cylinder member 21, and a rotor 22. And a plurality of vanes 25 capable of forming a plurality of compression chambers 24 inside the cylinder member 21 by being slidably attached to the inner peripheral surface 21a of the cylinder member 21.

  A cylinder chamber 27 is formed in the space between the cylinder member 21 and the rotor 22 to cause the refrigerant gas 26 to undergo a compression cycle by changing the volume of the compression chamber 24. A suction portion 28 capable of sucking the refrigerant gas 26 is provided upstream of the cylinder chamber 27 (in the rotation direction of the rotor 22), and a discharge portion 29 (main discharge) capable of discharging the refrigerant gas 26 downstream of the cylinder chamber 27. Part).

  On the other hand, the above-mentioned “oil separation unit 16” is not particularly described in detail, but is configured to separate the refrigerating machine oil contained in the refrigerant gas 26 compressed by the compression unit 15 using centrifugal force ( Centrifuge). As shown in FIG. 1, the oil separation portion 16 is attached to the other end side of a rear side block 32 to be described later and is housed in the body case 4. The heavy refrigerating machine oil separated by the oil separation unit 16 is accumulated at the bottom of the main body case 4, and the light refrigerant gas 26 from which the refrigerating machine oil has been separated is discharged to the outside through the upper space in the main body case 4. Is done.

  Next, details of the compression unit 15 will be described.

  The above-described “cylinder member 21” is attached to the inside of the other end side of the main body case 4 as shown in FIG. The cylinder member 21 is a disk-shaped member having a required thickness having an outer diameter substantially equal to the inner diameter of the main body case 4. A hollow portion for accommodating the rotor 22 is formed in the central portion of the cylinder member 21 so as to have the same shape in the axial direction. One end side and the other end side of the cylinder member 21 are closed while being sandwiched between the front side block 31 and the rear side block 32.

  The “front side block 31” and the “rear side block 32” are disk-like members having a required thickness and having an outer diameter substantially equal to the inner diameter of the main body case 4. The front side block 31 and the rear side block 32 are fitted in an airtight state to the inner peripheral surface 21a of the main body case 4 via a seal member, and the front side block 31 is fastened to the main body case 4 with a fastener such as a bolt. 33 is fastened and fixed. In addition, a locking wall portion 4 a capable of positioning and locking the front side block 31 in the axial direction of the rotary shaft 6 is provided inside the main body case 4.

  The front side block 31 and the rear side block 32 are respectively formed with shaft holes serving as the bearing portions 8 and 9 for supporting one end side of the rotary shaft 6.

  The suction part 28 is provided in the front side block 31, and the discharge part 29 is provided in the rear side block 32. As shown in FIG. 2, the “suction part 28” has a window-like suction port 28a for sucking the refrigerant gas 26 into the compression chamber 24, and a suction path 28b for guiding the refrigerant gas 26 to the suction port 28a. . On the other hand, the “discharge section 29” includes a discharge hole 29a for discharging the refrigerant gas 26 from the compression chamber 24, a discharge chamber 29b that can store the refrigerant gas 26 discharged from the discharge hole 29a, and the refrigerant gas 26 in the discharge chamber 29b. And a discharge passage 29c for guiding the oil to the outside (oil separation portion 16). A discharge valve 29d (check valve) is provided between the discharge hole 29a and the discharge chamber 29b.

  Further, the “rotor 22” described above is attached to the outer periphery of the other end side of the rotating shaft 6. In this case, the rotor 22 is a perfect circular disk having the same thickness as the cylinder member 21, and the rotation shaft 6 is attached to the center of the rotor 22 to rotate concentrically with the rotation shaft 6. It is supposed to be possible. Both end surfaces of the rotor 22 are in sliding contact with the inner surfaces of the front side block 31 and the rear side block 32 described above.

  The “vanes 25” described above are accommodated and disposed so as to protrude and be accommodated with respect to each of the plurality of vane grooves 35 provided at equal intervals in the circumferential direction with respect to the rotor 22. In this case, the number of vanes 25 is five and the number of vane grooves 35 is five. However, the number of vanes 25 and the number of installed vane grooves 35 are not limited thereto. The tip of the vane 25 has a curved shape so as to follow the inner peripheral surface 21 a of the cylinder member 21. The vane 25 and the vane groove 35 may extend in the radial direction of the rotor 22, or may have a required angle of inclination with respect to the radial direction of the rotor 22. A back pressure chamber 36 capable of applying a back pressure for projecting the vane 25 is formed in the inner part of the vane groove 35. A pair of vanes 25 adjacent to the space (cylinder chamber 27) between the rotor 22 and the cylinder member 21 are pressed by the tip of the vane 25 protruding by the back pressure against the inner peripheral surface 21 a of the cylinder member 21. The compression chamber 24 surrounded by is formed.

  Next, the path of the refrigerant gas 26 excluding the compression unit 15 will be described.

  As shown in FIG. 1, the compressor 1 is provided with a suction port 41 for refrigerant gas 26 and a discharge port 42 (not shown correctly). Among these, the suction port 41 is provided on the front cover 2, and the discharge port 42 is provided on the other end side of the main body case 4. The refrigerant gas 26 from the evaporator is supplied to the suction port 41, and the high-temperature and high-pressure refrigerant gas 26 is sent from the discharge port 42 toward the condenser. A low pressure chamber 43 (or a suction chamber) communicating with the suction port 41 is formed inside one end side of the main body case 4 provided with the motor unit 11, and the main body case 4 provided with the oil separation unit 16 is formed. A high pressure chamber 44 communicating with the discharge port 42 is formed inside the other end side.

  Furthermore, the low-pressure chamber 43 and the suction part 28 of the compression part 15 in the compressor part 12 are connected or communicated. On the other hand, the oil separation unit 16 in the high pressure chamber 44 and the discharge unit 29 of the compression unit 15 described above are connected or communicated directly or indirectly.

  And the path | route of the refrigerator oil in the compression part 15 is demonstrated.

  The rear side block 32 is provided with an oil guide passage 32 a for sending high-pressure refrigerating machine oil accumulated at the bottom of the high-pressure chamber 44 to the bearing portion 9 (shaft hole) substantially vertically. Further, back pressure is supplied to each vane 25 by sending refrigeration oil passing through a narrow gap between the bearing portion 9 and the rotary shaft 6 to the back pressure chamber 36 on the surface of the rear side block 32 on the rotor 22 side. A possible Saray groove 32b (back pressure supply circumferential groove) is formed.

  On the other hand, an oil guide passage (not shown) for sending the refrigerating machine oil branched from the oil guide passage 32a of the rear side block 32 to the front side block 31 is provided in the lower portion of the cylinder member 21 in the lateral direction. . The front side block 31 is provided with an oil guide passage (not shown) for sending refrigeration oil from the oil guide passage to the bearing portion 8 (shaft hole) substantially obliquely upward. In addition, on the surface of the front side block 31 on the rotor 22 side, the refrigerating machine oil that has passed through the narrow gap between the bearing portion 8 and the rotary shaft 6 is sent to the back pressure chamber 36, whereby back pressure is applied to each vane 25. A supplyable salai groove 31b (back pressure supply circumferential groove) is formed.

  As shown in FIG. 2, each of the above-described salai grooves 32b and salai grooves 31b are formed to extend as appropriate in the circumferential direction so as to communicate with the back pressure chamber 36 over an angular range in which the vanes 25 should be projected. .

  In this embodiment, the following structure is provided for the basic structure as described above.

(Configuration 1)
As shown in FIG. 2, the compression cycle of the refrigerant gas 26 is set to one for each compression chamber 24 by providing only one proximity portion 51 where the cylinder member 21 and the rotor 22 are close to each other. A single cylinder chamber 27 is formed which performs only once.

  Then, when the pressure of the refrigerant gas 26 in the compression chamber 24 reaches the discharge pressure P (see FIG. 3) on the upstream side (front side in the rotation direction) of the discharge portion 29, the pressure in the compression chamber 24 is released. Accordingly, at least one sub-discharge portion 54 that is held at the discharge pressure P is provided.

  Here, the proximity portion 51 described above is such that the cylinder member 21 and the rotor 22 have a slight clearance and are close to each other in a state that is almost close to contact.

  One or a plurality of the sub-ejection units 54 described above can be provided. Note that the sub-discharge unit 54 does not function effectively simply by being provided, and it is necessary to provide the sub-discharge part 54 at a position 55 where the pressure of the refrigerant gas 26 in the compression chamber 24 reaches the discharge pressure P in order to function effectively. is there.

  Similarly to the (main) discharge unit 29, the sub discharge unit 54 can store the discharge hole 54a for discharging the refrigerant gas 26 from the compression chamber 24 that has reached the discharge pressure P, and the refrigerant gas 26 discharged from the discharge hole 54a. A discharge chamber 54b, and a discharge passage 54c that guides the refrigerant gas 26 in the discharge chamber 54b to the outside (oil separation unit 16). A discharge valve or a pressure relief valve 54d (check valve) is provided between the discharge hole 54a and the discharge chamber 54b.

  Hereinafter, the cylinder chamber 27 will be described.

  First, in the cylinder chamber 27, the shape of the inner peripheral surface 21a of the cylinder member 21 increases in volume from the proximity portion 51 or the suction portion 28 to the substantially maximum interval portion 52 (volume increasing portion), and is almost at the maximum. The volume is set so that the volume generally decreases from the interval portion 52 toward the discharge portion 29 or the proximity portion 51 (volume reduction portion). The volume of the compression chamber 24 is maximized at one point where the vanes 25 on both sides of the compression chamber 24 sandwich the maximum gap portion 52, but this position differs depending on the shape of the cylinder chamber 27.

  In the compression cycle of the refrigerant gas 26, an intake stroke for sucking the refrigerant gas 26, a compression stroke for compressing the refrigerant gas 26, and a discharge stroke for discharging the refrigerant gas 26 are performed in order (each compression). It is repeated once per revolution for each chamber 24. For example, when there are five compression chambers 24, it is repeated a total of five times per revolution). Thus, the suction stroke is performed, and the compression stroke and the discharge stroke are performed in the volume reducing portion.

  More specifically, a section from when the vane 25 on the front side in the rotation direction of the cylinder chamber 27 passes the position upstream of the suction port 28a to when the rear vane 25 passes the position downstream of the suction port 28a. Is the inhalation stroke. Further, the interval from when the pressure of the refrigerant gas 26 in the compression chamber 24 reaches the discharge pressure and the discharge valve 29d or the pressure release valve 54d opens until the rear vane 25 passes through the discharge hole 29a is the discharge stroke. A section between the suction stroke and the discharge stroke is a compression stroke. Note that the suction port 28a and the discharge hole 29a are provided at positions slightly shifted from the proximity portion 51 to the downstream side and the upstream side, and the high-pressure refrigerant gas being discharged is between the discharge stroke and the suction stroke. 26 and the low-pressure refrigerant gas 26 being sucked are sealed. Therefore, the proximity part 51 described above can seal between the high-pressure refrigerant gas 26 and the low-pressure refrigerant gas 26 described above. As described above, the compression cycle in the single cylinder chamber 27 is performed in an angle range slightly smaller than 360 [degrees].

  Further, the sub-discharge section 54 is set around the position 55 where the pressure of the refrigerant gas 26 in the compression chamber 24 reaches the discharge pressure P in the latter half of the compression stroke. Then, when the discharge pressure P is reached, the vane 25 on the front side in the rotation direction of the compression chamber 24 passes through the sub-discharge portion 54 or the discharge portion 29, so that the compression chamber 24 is connected to the sub-discharge portion 54 or the discharge portion 29. Try to communicate. In this case, the position 55 reaching the discharge pressure P is set to a position where the vane 25 on the front side in the rotation direction of the compression chamber 24 is at an angle of 270 degrees from the proximity portion 51 or a position further downstream than that. ing. This position is changed depending on the operating conditions. However, the position 55 that reaches the discharge pressure P is not limited to this, and varies depending on the shape of the cylinder chamber 27. The shape of the inner peripheral surface 21a of the cylinder member 21 is so set that the refrigerant gas 26 in the compression chamber 24 is gradually compressed to the discharge pressure P with a small amount of power until the position 55 at which the discharge pressure P is reached. Set. Thereby, the inner peripheral surface 21a of the cylinder member 21 has an asymmetric shape as illustrated. However, this compression need not be unnecessarily gradual.

(Configuration 2)
In the above, the sub-ejection unit 54 is installed with an interval 56 that is the same as or slightly narrower than the tip of the adjacent vane 25 with respect to the adjacent ejection unit 29 or the sub-ejection unit 54. To do.

  In this case, since there are five vanes 25, the distance between the sub-discharge part 54 and the adjacent discharge part 29 or the sub-discharge part 54 (in this case, the angle interval is used, but the distance is Is also set to approximately 72 [degrees] or less obtained by dividing an angle 360 [degree] of one round by 5. Alternatively, when four vanes 25 are provided, the interval 56 is set to approximately 90 [degrees] obtained by dividing an angle 360 [degrees] of one round by 4 or less. When the number of vanes 25 is other than the above, the interval 56 is set in the same manner as described above.

  In accordance with the above, the position of the sub-discharge portion 54 and the position 55 reaching the discharge pressure P are set so as to be a position that is an integral multiple of the interval 56 from the discharge portion 29 or a position slightly narrower than that. To do. Of course, the above-mentioned “integer multiple” includes a significant error.

  The interval between the discharge unit 29 and the sub-discharge unit 54 in the configuration 2 is a rotation axis between the center position of the discharge hole 29a of the discharge unit 29 and the center position of the discharge hole 54a of the sub-discharge unit 54. 6 or an interval (length) along the inner peripheral surface 21a of the cylinder member 21, while the interval between the tips of adjacent vanes 25, 25 partitions one compression chamber 24. The angle between the centers of the two vanes 25, 25 around the rotation axis 6 or the distance (length) along the inner peripheral surface 21 a of the cylinder member 21.

  Similarly, the interval between the sub-ejection part 54 and another sub-ejection part 54 in Configuration 2 is the center position of the ejection hole 54a of the sub-ejection part 54 and the center of the ejection hole 54a of the sub-ejection part 54. The angle between the position and the position around the rotation axis 6 or the distance (length) along the inner peripheral surface 21 a of the cylinder member 21.

(Configuration 3)
In the above, as shown in FIG. 4A, the sub-discharge portion 54 is formed between the discharge hole 29 a of the discharge portion 29 and the discharge hole 54 a of the sub-discharge portion 54, which are arranged along the rotation direction of the vane 25. The distance (length) L2 along the inner peripheral surface 21a of the cylinder member 21 between the closest edge portions 29e and 54e is the tip of the two vanes 25 and 25 that follow each other along the rotation direction. The contact points 25a, 25a that are in contact with the inner peripheral surface 21a of the member 21 are installed so as to be shorter than the distance (length) L1 along the inner peripheral surface 21a of the cylinder member 21 (L2 <L1). Yes.

  4A shows the inner peripheral surface 21a of the cylinder member 21 in a planar shape, and the posture and position where the vanes 25 and 25 are both orthogonal to and parallel to the inner peripheral surface 21a. Although described in the relationship, this is due to the convenience of schematically explaining the configuration 3. To be exact, as shown in FIG. 2, the inner peripheral surface 21 a of the cylinder member 21 is formed on the rotor 22. The volume of the compression chamber 24 is gradually reduced with rotation, and the vanes 25 and 25 are in a posture and positional relationship with an inclination angle of 72 degrees.

  Further, in the case where two or more sub-discharge sections 54 are installed, as shown in FIG. 4 (b), two sub-discharge sections 54, 54 that follow each other along the rotation direction of the vane 25 are further included. An interval (length) L4 along the inner peripheral surface 21a of the cylinder member 21 between the adjacent edge portions 54e, 54e of the discharge holes 54a, 54a is two vanes 25 that follow each other in the rotational direction. The distance (length) L3 along the inner peripheral surface 21a of the cylinder member 21 between the contact points 25b and 25b at which the tips of the 25 contact the inner peripheral surface 21a of the cylinder member 21 is shorter (L4 <L3). So that it is installed.

(Configuration 4)
In the above configurations 1 to 3, in particular, the sub-discharge portion 54 and the adjacent discharge portion 29 or the sub-discharge portion 54 are set at an interval 56 at which the discharge of the refrigerant gas 26 from the compression chamber 24 is not interrupted. To do. In particular, “slightly narrow” in the configuration 2 considers an adjustment allowance for preventing the discharge of the refrigerant gas 26 from the compression chamber 24 from being interrupted.

  In this case, in order to prevent the discharge from being interrupted due to the thickness of the vane 25, the interval 56 (angular interval or the like) is substantially equal to the thickness of the vane 25 than the interval between the tips of the adjacent vanes 25. It is set to be narrowed by about half to one sheet. It should be noted that the interval 56 is meaningless simply because it is simply narrowed, and the function cannot be effectively exhibited.

(Configuration 5)
In the above description, the maximum distance portion 52 in which the distance in the radial direction between the cylinder member 21 and the rotor 22 in the cylinder chamber 27 is maximum is set to a position closer to the front side than the angle 90 [degrees] in the rotation direction from the above-described proximity portion 51. Set.

  Preferably, the above-mentioned maximum interval portion 52 is positioned as close to the proximity portion 51 as possible within a range in which a necessary intake amount of the refrigerant gas 26 can be secured in a section through which the upstream vane 25 passes in the intake stroke. Set to.

<Action>
The operation of this embodiment will be described below.

  First, compression of the refrigerant gas 26 will be described.

  The refrigerant gas 26 supplied from the evaporator and taken into the compressor 1 from the suction port 41 passes through the low pressure chamber 43 from the suction portion 28 provided in the front side block 31 and the rotor 22 of the compression portion 15. It is sent to a space (cylinder chamber 27) between the cylinder member 21 and supplied in turn to the compression chambers 24 surrounded by the adjacent vanes 25 inside the space. The refrigerant gas 26 supplied to each compression chamber 24 is sent to a discharge unit 29 provided in the rear side block 32 while being compressed by the rotation of the rotor 22, and is discharged from the discharge unit 29, and also passes through the oil separation unit 16. To the high pressure chamber 44, taken out from the high pressure chamber 44 through the discharge port 42, and sent to the condenser on the downstream side.

  At this time, in the compression unit 15, one compression cycle for each compression chamber 24 is performed in the space between the rotor 22 and the cylinder member 21 in the portion between the suction unit 28 and the discharge unit 29. A cylinder chamber 27 to be performed is formed, and by this compression cycle, a suction stroke, a compression stroke, and a discharge stroke are sequentially performed for each compression chamber 24 to obtain a high-temperature and high-pressure refrigerant gas 26.

  Next, the flow of refrigeration oil in the compressor unit 12 will be described.

  The high-pressure refrigerating machine oil separated from the refrigerant gas 26 by the oil separation unit 16 and accumulated at the bottom of the high-pressure chamber 44 passes through the oil guide path 32a provided in the rear side block 32 in the substantially vertical direction, and the bearing unit 9 ( Through the narrow gap between the bearing portion 9 and the rotary shaft 6 and sent to the Sarai groove 32b (back pressure supply peripheral groove portion) provided on the rotor 22 side surface of the rear side block 32, The back pressure is supplied from the salai groove 32 b to the back pressure chamber 36 to supply back pressure to each vane 25.

  Similarly, the refrigerating machine oil in the oil guide passage 32 a of the rear side block 32 passes through the oil guide passage provided in the cylinder member 21 in the lateral direction and the oil guide passage provided in the front side block 31 obliquely upward. The salai groove 31b (back pressure supply circumference) provided on the rotor 22 side surface of the front side block 31 through the narrow gap between the bearing portion 8 and the rotary shaft 6 is sent to the bearing portion 8 (shaft hole). Are supplied to the back pressure chamber 36 from the Sarai groove 31b and supply back pressure to each vane 25.

  The vane 25 is urged and protruded by the high-pressure refrigeration oil supplied to the back pressure chamber 36 and the centrifugal force.

  The refrigerating machine oil supplied to the back pressure chamber 36 enters each compression chamber 24 through a narrow gap between the vane 25 and the vane groove 35 and is accompanied by the refrigerant gas 26 in the compression chamber 24 to separate the oil. The oil separation unit 16 separates the refrigerant gas 26 from the refrigerant gas 26 and repeats the above.

  Next, the operation of the characteristic part of this embodiment will be described.

  As a comparative example 1, for example, in the case of a normal vane rotary type compressor, the proximity part 51 between the cylinder member 21 and the rotor 22 is set at two positions in the diametrical direction, and the proximity part 51 and the proximity part 51 are Two cylinder chambers 27 are formed between them, and the inner peripheral surface 21a of the cylinder member 21 has a short diameter at the position of the proximity portion 51 and a long diameter at a position advanced 90 degrees from the proximity portion 51 in the rotational direction. The compression cycle is performed twice per revolution for each compression chamber 24 as a symmetrical shape such as an oval or an ellipse (for example, if there are five compression chambers 24, the compression cycle is repeated a total of 10 times per revolution). I have to.

  In this way, for example, in the compression cycle of the first cylinder chamber 27, as shown by the line A1 in FIG. 3, the refrigerant gas 26 is rapidly compressed during a half circumference, so a large amount of power is required. become. In addition, it is unavoidable that overcompression A2 occurs before the discharge of the refrigerant gas 26 starts.

  Further, as Comparative Example 2, if the vane rotary type compressor is simply arranged with one cylinder chamber 27 and the compression cycle is performed once for each compression chamber 24, for example, FIG. 3, the compression timing of the refrigerant gas 26 is delayed by half a cycle compared to the line A1, as indicated by the line B1. Power is needed. In addition, it is unavoidable that over-compression B2 occurs before the refrigerant gas 26 starts to be discharged.

  On the other hand, in the vane rotary type compressor according to this embodiment, as described above, the cylinder chamber 27 is unified by setting the proximity portion 51 at one place in the circumferential direction, and the inner peripheral surface of the cylinder member 21. 21a is made into a shape (asymmetrical shape) capable of gently compressing the refrigerant gas 26 over one round.

  In addition, by setting the position of the maximum interval portion 52 to the near side from the adjacent portion 51 in the rotational direction with respect to the angle 90 [degrees], the refrigerant gas 26 can be sucked in earlier and can be compressed longer and gently. (See line C1 in FIG. 3). Thereby, the power required for compression can be reduced.

  As is well known, since the pressure and volume of the gas are inversely proportional, it is extremely difficult to compress the gas so that the pressure increases proportionally over the entire compression stroke.

  For this reason, in the first half of the compression stroke indicated by the line C1 in FIG. 3, since the change in pressure is reduced even if the volume is greatly reduced, the compression starts at an earlier timing than the lines A1 and B1, and the lines A1 and The refrigerant gas 26 is compressed so as to be gentler than B1 but not excessively gentle so that both power reduction and efficient compression can be achieved. Further, in the latter half of the compression stroke indicated by line C2 in FIG. 3, the pressure changes greatly even if the volume is slightly reduced. Therefore, the shape of the cylinder chamber 27 is adjusted to be gentler than the lines A1 and B1. In addition, the refrigerant gas 26 is compressed so that the inclination is as constant as possible so that the volume is gradually reduced. At this time, the joint between the line C1 and the line C2 is changed gently. Thus, the overcompression C3 can be reduced by making the slope of the line C2 gentle.

  Further, in the discharge stroke indicated by the line C4 in FIG. 3, when the inside of the compression chamber 24 reaches the discharge pressure P, the discharge is discharged from the sub discharge portion 54, whereby the inside of the compression chamber 24 is held at a constant discharge pressure P. It will be. As a result, the discharge stroke starts early and is lengthened so that over-compression (see line C3 in FIG. 3) can be prevented. Then, the ejection from the ejection unit 29 is performed following the ejection from the sub-ejection unit 54.

  FIG. 3 is a graph showing the relationship between the pressure in the compression chamber 24 and the rotation angle. The rotation angle is based on the angle of the vane 25 on the front side of the compression chamber 24.

<Effect>
According to this embodiment, the following effects can be obtained.

(Effect 1)
By unifying the cylinder chamber 27 and performing the compression cycle of the refrigerant gas 26 only once per rotation for each compression chamber 24, the refrigerant gas 26 can be gently compressed. As a result, the required power can be reduced and the differential pressure between the adjacent compression chambers 24 can be reduced to prevent the refrigerant gas 26 from leaking from the vane 25 and reducing the volume efficiency.

  Further, by providing at least one or more sub-discharge sections 54 on the upstream side (the optimal position) of the discharge section 29, when the pressure of the refrigerant gas 26 in the compression chamber 24 reaches the discharge pressure P, the sub-discharge section Since the pressure of the compression chamber 24 can be removed from the pressure chamber 54 and maintained at the discharge pressure P, it is possible to reliably prevent the compression chamber 24 from being over-compressed. As a result, wasteful power consumption due to overcompression can be suppressed and efficiency can be improved. Further, since the discharge timing of the refrigerant gas 26 is advanced, the discharge efficiency can be improved accordingly.

  As described above, the efficiency (coefficient of performance or COP (Coefficient Of Performance)) of the vane rotary type compressor as a whole can be improved.

(Effect 2)
By disposing the sub-discharge portion 54 and the adjacent discharge portion 29 or the sub-discharge portion 54 at an interval 56 that is the same as or slightly narrower than the tip of the adjacent vane 25, It becomes possible to arrange efficiently in the position required for prevention of compression.

(Effect 3)
In the present embodiment, the sub-discharge portion 54 extends along the inner peripheral surface 21a of the cylinder member 21 between the edge portions 29e and 54e between the discharge hole 29a of the discharge portion 29 and the discharge hole 54a of the sub-discharge portion 54. The distance (length) L2 is the distance (length) along the inner peripheral surface 21a of the cylinder member 21 between the contact points 25a, 25a of the two vanes 25, 25 with the inner peripheral surface 21a of the cylinder member 21. ) According to the installed configuration 3 so as to be shorter than L1 (L2 <L1), the compression chamber 24 defined by the two vanes 25 and 25 that follow each other along the rotation direction is The stage before facing the discharge hole 29a, the stage before facing the discharge hole 54a of the sub-discharge section 54, and before the vane 25 on the upstream side (rear side) in the rotation direction of the compression chamber 24 passes the discharge hole 54a of the sub-discharge section 54. In the compression chamber 24 Since the vanes 25 of the downstream side (front side) of a state facing the discharge port 29a of the discharge portion 29, the auxiliary discharge portion 54, it is possible to efficiently place the required position to prevent over-compression.

  Further, in the present embodiment, there are two or more sub-discharge portions 54 installed, and the cylinder member 21 between the edge portions 54e and 54e of the discharge holes 54a and 54a of the two sub-discharge portions 54 and 54 is provided. The inner peripheral surface of the cylinder member 21 between the contact points 25b, 25b of the two vanes 25, 25 contacting the inner peripheral surface 21a of the cylinder member 21 is a distance (length) L4 along the inner peripheral surface 21a. According to the configuration 3 in which the sub-discharge sections 54 and 54 are installed so as to be shorter than the interval (length) L3 along the line 21a (L4 <L3), the two vanes 25 that follow each other along the rotation direction. , 25, the discharge chamber 54 discharges from the upstream (rear side) secondary discharge portion 54 in the rotational direction before it faces the discharge hole 54a of the downstream (front side) secondary discharge portion 54 in the rotational direction. Facing the hole 54a, the compression chamber 24 Before the vane 25 on the upstream side in the rotation direction passes through the discharge hole 54 a of the upstream sub-discharge portion 54, the vane 25 on the downstream side in the rotation direction of the compression chamber 24 discharges the discharge hole 54 a in the sub-discharge portion 54 on the downstream side. Therefore, both the sub-discharge sections 54 and 54 can be efficiently arranged at positions necessary for preventing overcompression.

  FIG. 4 shows the distance (length) L2 between the adjacent edges of the discharge holes of the two discharge portions, and the distance between the contact points where the tips of the two vanes contact the inner peripheral surface of the cylinder member ( Two discharge sections are set so that the length is shorter than L1 (L2 <L1). An embodiment of the gas compressor according to the present invention is shown in FIG. As described above, the sub-ejection part 54 has the edge parts 29f and 54f that are farthest from each other between the ejection hole 29a of the ejection part 29 and the ejection hole 54a of the sub-ejection part 54 that follow each other along the rotation direction of the vane 25. The distance (length) L2 ′ (> L2) along the inner peripheral surface 21a of the cylinder member 21 between the tips of the two vanes 25 and 25 that follow each other in the rotational direction is also within the cylinder member 21. Cylinder portion between contact points 25a, 25a that are in contact with the peripheral surface 21a Shorter than the distance (length) L1 along the inner circumferential surface 21a of 21 (L2 '<L1) may be one that is installed to.

  What is configured in this way is that even when the discharge hole facing the compression chamber 24 is switched, that is, when the tip of the vane 25 passes through the discharge hole, the tip of the vane 25 is inclined as shown in the figure. Since the cross-sectional area of the portion serving as the discharge passage is not reduced, the discharge operation can be continued more smoothly.

  Similarly, even in the case where two or more sub-discharge sections 54 are installed, as shown in FIG. 5B, two sub-discharge sections 54 and 54 that follow each other along the rotation direction of the vane 25 are also illustrated. The distance (length) L4 ′ (> L4) along the inner peripheral surface 21a of the cylinder member 21 between the adjacent edge portions 54f, 54f of the discharge holes 54a, 54a is The distance between the contact points 25b, 25b where the tips of the two vanes 25, 25 contact the inner peripheral surface 21a of the cylinder member 21 is shorter than the distance (length) L3 along the inner peripheral surface 21a of the cylinder member 21. (L4 ′ <L3) may be installed.

(Effect 4)
By arranging the sub-discharge portion 54 and the adjacent discharge portion 29 or the sub-discharge portion 54 at an interval 56 where the discharge of the refrigerant gas 26 from the compression chamber 24 is not interrupted, the refrigerant gas 26 from the compression chamber 24 is disposed. It is possible to prevent over-compression from occurring during the discharge of the gas.

(Effect 5)
The maximum distance portion 52 in which the distance in the radial direction between the cylinder member 21 and the rotor 22 in the cylinder chamber 27 is maximized is set to a position on the nearer side than the angle 90 [degrees] in the rotation direction from the proximity portion 51 described above. As a result, the suction stroke can be started at an earlier timing, thereby making it possible to advantageously perform the compression stroke and the discharge stroke and improve the efficiency. For example, the compression stroke can be lengthened or slowed, the discharge stroke can be started earlier, or the length can be lengthened.

  Although the embodiments of the present invention have been described in detail with reference to the drawings, the embodiments are only examples of the present invention, and the present invention is not limited to the configurations of the embodiments. Needless to say, design changes and the like within a range not departing from the gist of the invention are included in the present invention. Further, for example, when each embodiment includes a plurality of configurations, it is a matter of course that possible combinations of these configurations are included even if not specifically described. Further, when a plurality of embodiments and modifications are shown, it is needless to say that possible combinations of configurations extending over these are included even if not specifically described. Further, the configuration depicted in the drawings is of course included even if not particularly described. Further, when there is a term of “etc.”, it is used in the sense that the equivalent is included. In addition, when there are terms such as “almost”, “about”, “degree”, etc., they are used in the sense that they include those in the range and accuracy recognized by common sense.

1 Compressor (gas compressor)
21 Cylinder member 22 Rotor 24 Compression chamber 25 Vane 26 Refrigerant gas (gas)
27 Cylinder chamber 28 Suction part 29 Discharge part 51 Proximity part 52 Maximum distance part 56 Distance 54 Sub-discharge part P Discharge pressure

Claims (5)

A hollow cylinder member, a rotor that is rotatably disposed inside the cylinder member, and a protrusion that is slidably mounted on the rotor and has a tip that is in sliding contact with the inner peripheral surface of the cylinder member, thereby A plurality of vanes capable of forming a plurality of compression chambers therein are formed, and a cylinder chamber is formed between the cylinder member and the rotor to perform a gas compression cycle by changing the volume of the compression chamber. In the gas compressor provided with a suction part capable of sucking the gas upstream of the cylinder chamber and provided with a discharge part capable of discharging the gas downstream.
A single cylinder chamber in which the compression cycle of the gas is performed only once per round for each compression chamber is formed between the cylinder member and the rotor by providing only one close portion where the two are close to each other. And
At least one or more sub-discharge sections are provided on the upstream side of the discharge section to maintain the discharge pressure by releasing the pressure of the compression chamber when the pressure of the gas in the compression chamber reaches the discharge pressure. A gas compressor characterized by that.   The said sub discharge part is installed in the adjacent discharge part or the sub discharge part with the space | interval which is the same as between the front-end | tips of an adjacent vane, or slightly narrower than it. The gas compressor described.   The distance along the inner peripheral surface of the cylinder between the adjacent edge portions between the discharge portion and the sub discharge portion that move back and forth along the rotation direction of the vane, or in the rotation direction of the vane The distance along the inner peripheral surface of the cylinder between the adjacent edges between the two sub-ejection parts that follow each other along the inner circumferential surface of the cylinder is the tip of the two vanes that follow each other along the rotation direction. 2. The sub-discharge portion is installed so as to be shorter than an interval along the inner peripheral surface of the cylinder between contact points that respectively contact the inner peripheral surface of the cylinder. The gas compressor described.   4. The gas compressor according to claim 2, wherein the sub-discharge portion and the adjacent discharge portion or the sub-discharge portion are arranged at intervals at which the discharge of the gas from the compression chamber is not interrupted. 5. .   In the cylinder chamber, the maximum gap portion where the gap in the radial direction between the cylinder member and the rotor is maximized is set at a position closer to the rotation direction than the angle 90 [degrees] from the proximity portion. The gas compressor according to any one of claims 1 to 4.