JP5878911B2 - Gas compressor - Google Patents

Description

  The present invention relates to an eccentric gas compressor having a rotor and a vane.

  Various eccentric gas compressors have been conventionally proposed as shown in Patent Document 1.

  As shown in FIG. 6, the gas compressor 100 includes a housing 102, a compression unit 103, and a drive unit 104 that transmits driving force to the compression unit 103.

  The compression unit 103 is fixed to the cylinder block 106 in which the cylinder chamber 106 a is formed on the inner periphery, the side block 108 including the front side block 108 a and the rear side block 108 b, the rotor 107 accommodated in the cylinder chamber 106 a, and the rotor 107. Drive shaft 105, oil 109 that maintains lubricity in the gas compressor 100, and a back pressure control device 114 that supplies pressure to a vane groove (not shown) formed in the rotor 107.

  In such a conventional gas compressor 100, a vane (not shown) is housed in a vane groove formed in the rotor 107 so that the vane can protrude and retract, the vane protrudes from the vane groove, and the tip of the vane is the inner wall of the cylinder chamber 106a. And the rotor 107 rotates to compress the gas (refrigerant) in the cylinder chamber 106a.

  Further, the side block 108 includes an oil groove 110 that cuts off and communicates with the vane groove, and an oil supply path 112a.

  The oil supply path 112a supplies the high-pressure oil 109 to the vane groove through the oil groove 110 only when the gas compressor 100 is driven under the control of the back pressure control device 114, and the pressure for the vane to protrude from the vane groove. Supply.

JP 2006-132370 A

  However, in the conventional gas compressor 100, as shown in FIG. 6, the oil groove 110 is provided in the rear side block 108b. Accordingly, since the hydraulic pressure in the oil groove 110 acts only on one side of the rotor 107, an offset load acts on the rotor 107.

  Then, since the end of the rotor 107 comes into contact with the end surfaces of the front side block 108a and the rear side block 108b due to the inclination of the rotor 107, the sliding resistance increases, the end surface of the side block 108 wears, and the airtightness of the compression unit 103 is increased. May be hindered.

  Accordingly, the present invention has been made to solve the above-described problems, and an object of the present invention is to provide a gas compressor capable of supplying pressure to the vane groove and preventing an uneven load from acting on the rotor. It is said.

  In order to solve the above problems, in the present invention, a cylinder chamber 35 is provided in the cylinder block 23 by sandwiching the cylinder block 23 by a pair of side blocks 25, the cylinder chamber 35 is rotatable, and A rotor 29 having an eccentric position in the cylinder chamber 35 as a rotation center is provided, and vanes 31 are provided in a plurality of vane grooves 71 opened in the outer peripheral surface of the rotor 29 so as to protrude freely. A compression chamber 35a is formed by two adjacent vanes 31 protruding from the vane groove 71. A back pressure space 73 is formed in the vane groove 71 of the rotor 29 on the back side of the vane 31, and the pair of side blocks 25, pressure supply grooves 46 and 62 are provided at both end faces 39 and 53, and back pressure is supplied to the back pressure space 73 from the pressure supply grooves 46 and 62. In the compressor 1, the pressure supply grooves 46 and 62 are provided at symmetrical positions of both end faces 39 and 53 of the pair of side blocks 25, and are formed in the back pressure space 73 at the first half position of the compression chamber 35 a. An intermediate pressure supply groove 47, 63 that opens and supplies an intermediate pressure that is lower than the discharge pressure and higher than the suction pressure, and provided at symmetrical positions of both end faces 39, 53 of the pair of side blocks 25, are compressed in the compression chamber 35a. The back pressure space 73 is opened at the latter half position, and is composed of high pressure supply grooves 49, 65 for supplying discharge pressure. The high pressure supply grooves 49, 65 on one side have oil supply passages 37, 43, 67a, 67b. The oil O stored in the oil sump 21 is supplied via the communication passage 61, and the high pressure supply groove 49 on one side is connected to the high pressure supply grooves 49 and 65 on the other side via the back pressure space 73 of the rotor 29. , 65 to supply oil O It is characterized in.

  According to the present invention, since the intermediate pressure supply groove and the high pressure supply groove are provided at the symmetrical positions of the pair of side blocks, the intermediate pressure and the high pressure act on the symmetrical positions of the side surfaces on both sides of the rotor. It can be prevented from acting.

  In addition, since high pressure can be supplied from one high pressure supply groove to the other high pressure supply groove via the back pressure space, there is no need to provide a communication path that connects the high pressure supply groove and the oil supply path. Processing is easy and the manufacturing cost can be reduced.

The whole sectional view of the gas compressor of the present invention. The principal part expanded sectional view of the gas compressor shown in FIG. AA sectional view taken on the line in FIG. The BB arrow directional view shown in FIG. The CC arrow directional view shown in FIG. The whole sectional view of the conventional gas compressor.

  Hereinafter, embodiments of the present invention will be described in detail with reference to FIGS.

[First Embodiment]
As shown in FIG. 1, the gas compressor 1 of the first embodiment is a so-called eccentric compressor, and includes a cylindrical housing 2 and a compression unit 3 that is accommodated in the housing 2 and compresses gas (refrigerant). And a motor unit 4 that generates a rotational driving force by a magnetic force, and an inverter unit 5 that controls the driving of the motor unit 4.

  The housing 2 includes a front head 7 in which a suction port (not shown) is formed, and a bottomed cylindrical rear case 9 whose opening is closed by the front head 7.

  The inverter unit 5 is fixed to the outside of the front head 7, and the end of the drive shaft 33 of the compression unit 3 is rotatably supported inside the front head 7.

  In the rear case 9, the inside of the housing 2 is sealed by closing the opening with the front head 7, the compression portion 3 is fixed to the inner wall 15, and a suction chamber 13 and a discharge chamber 17 are formed in the rear case 9. Is done. A discharge port (not shown) is formed on the outer periphery of the rear case 9.

  In the suction chamber 13, the gas (refrigerant) sucked by the suction port flows and the motor unit 4 is arranged.

  In the discharge chamber 17, the refrigerant compressed by the compression unit 3 is discharged, and an oil reservoir 21 in which oil O for maintaining lubricity in the housing 2 is stored is formed on the lower side. Further, the compressed refrigerant is discharged from the discharge port formed on the outer periphery of the rear case 9 through the discharge chamber 17.

  As shown in FIG. 2, the compression unit 3 includes a cylinder block 23 in which a cylinder chamber 35 is formed on the inner periphery, a pair of side blocks 25 arranged so as to sandwich both ends of the cylinder block 23, and one side The oil separator 27 fixed to the block 25, the rotor 29 rotatably accommodated in the cylinder chamber 35, the vane 31 accommodated in a vane groove 71 formed in the rotor 29, and one end side is a pair. A drive shaft 33 is rotatably supported by the side block 25 and is rotatably supported by the front head 7 at the other end.

  As shown in FIG. 3, the cylinder block 23 includes a cylinder chamber 35 having a distorted circumferential shape, a discharge hole 34 for discharging the refrigerant compressed in the cylinder chamber 35, and an opening / closing arranged to close the discharge hole 34. A free discharge valve 36, a discharge hole 38 for discharging the refrigerant discharged from the discharge hole 34 to the discharge chamber 17, and a cylinder-side oil supply path 37 communicating with the oil supply paths 43 and 67b of the side block 25 are provided. Yes.

  In the cylinder chamber 35, a compression chamber 35 a is formed in the cylinder chamber 35 by the adjacent vane 31 protruding from the inner peripheral surface of the cylinder chamber 35 and the vane groove 71 of the rotor 29.

  The discharge holes 34 are provided in the cylinder chamber 35 so as to open at two places, and the refrigerant compressed in the cylinder chamber 35 is discharged from the discharge holes 34 respectively.

  The discharge valve 36 disposed so as to close the discharge hole 34 opens and closes the valve body by the pressure of the refrigerant compressed in the cylinder chamber 35.

  As shown in FIGS. 2, 4, and 5, the pair of side blocks 25 includes a front side block 25 a on the front head 7 side and a rear side block 25 b on the bottom surface side of the rear case 9.

  As shown in FIGS. 2 and 5, the front side block 25 a supplies the refrigerant sucked into the suction chamber 13 to the rotor chamber end surface 39 fixed to one end surface of the cylinder block 23 and supplies the refrigerant to the cylinder chamber 35. A suction hole 40, a front side bearing 41 that rotatably supports the drive shaft 33, and a front side oil supply passage 43 that supplies pressure to the front side bearing 41 are provided.

  Two pressure supply grooves 46 are provided on the rotor side end surface 39 of the front side block 25 a in the circumferential direction of the rotor side end surface 39.

  The pressure supply groove 46 includes an intermediate pressure supply groove 47 that supplies an intermediate pressure that is lower than the discharge pressure and higher than the suction pressure, and a high-pressure supply groove 49 that supplies the discharge pressure, and is formed on the back side of the vane 31. Back pressure is supplied to the back pressure space 73 to be generated.

  The intermediate pressure supply groove 47 applies a pressure that causes the vane 31 to protrude from the vane groove 71 by supplying oil O that has become an intermediate pressure to the back pressure space 73.

  The high-pressure supply groove 49 supplies a pressure higher than the intermediate pressure supplied from the intermediate pressure supply groove 47 to the back pressure space 73, thereby applying a pressure that causes the vane 31 to protrude from the vane groove 71. ing.

  An annular front side annular groove 51 is formed in the front side bearing 41 and is provided so as to communicate with the front side oil supply passage 43 on one end side. Further, the front-side oil supply path 43 on the other end side communicates with the cylinder-side oil supply path 37 of the cylinder block 23.

  As shown in FIGS. 2 and 4, the rear side block 25 b includes a rotor side end surface 53 fixed to the other end surface of the cylinder block 23, and a discharge side on which the oil separator 27 is fixed on the rotor side end surface 53 and the other side. An end face 55, an oil supply hole 57 formed in the lower part in FIG. 2, a discharge hole 58 for discharging the refrigerant compressed in the cylinder chamber 35 to the discharge chamber 17, and a rear side that rotatably supports the drive shaft 33. A bearing 59 and a communication passage 61 for supplying pressure to a back pressure space 73 described later are provided. The rear side bearing 59 is formed with an annular rear side annular groove 69 similar to the front side bearing 41, and the rear side annular groove 69 communicates with the communication path 61.

  Two pressure supply grooves 62 are provided in the circumferential direction of the rotor-side end surface 53 on the rotor-side end surface 53 of the rear side block 25b.

  The pressure supply groove 62 includes an intermediate pressure supply groove 63 that supplies an intermediate pressure that is lower than the discharge pressure and higher than the suction pressure, and a high pressure supply groove 65 that supplies the discharge pressure (high pressure).

  The pressure supply grooves 46 and 62 respectively provided in the front side block 25a and the rear side block 25b are provided at symmetrical positions with the cylinder block 23 interposed therebetween, and are provided in the same shape.

  The rear side block 25b communicates with the oil supply hole 57 to form rear side oil supply passages 67a and 67b. The rear side oil supply passage 67a communicates with the rear side annular groove 69 to provide rear side oil. The supply path 67 b communicates with the cylinder side oil supply path 37 of the cylinder block 23.

  A cylinder chamber 35 is formed on the inner peripheral side of the cylinder block 23 by sandwiching both ends of the cylinder block 23 by the front side block 25a and the rear side block 25b.

  As shown in FIG. 3, the rotor 29 is disposed so that one location is in contact with the inner wall of the cylinder chamber 35, and the rotor 29 is disposed at a position shifted from the center (centroid) of the cylinder chamber 35.

  The columnar rotor 29 accommodated rotatably in the cylinder chamber 35 includes a vane groove 71 in which a plurality of vanes 31 opened on the outer peripheral surface of the rotor 29 are accommodated in a projecting manner, and a back pressure space on the back side of the vane 31. 73. Further, both ends of the rotor 29 are arranged in sliding contact with the rotor side end faces 39 and 53 of the pair of side blocks 25.

  As the rotor 29 rotates, the back pressure space 73 formed in the rotor 29 communicates with the intermediate pressure supply grooves 47 and 63 at the first compression position, and communicates with the high pressure supply grooves 49 and 65 at the second compression position. .

  The drive shaft 33 to which the rotor 29 and the motor rotor 8 of the motor unit 4 are fixed is rotatably supported at one end by a pair of side blocks 25 and is rotatably supported by the front head 7 at the other end.

  The motor unit 4 serving as a driving source for the compression unit 3 includes a stator 6 fixed to the inner wall 15 of the rear case 9 and a motor rotor 8 that is rotatably arranged on the inner peripheral side of the stator 6 and rotates by magnetic force. Yes. The motor rotor 8 is rotated by the magnetic force, so that the rotational driving force is transmitted to the compression unit 3.

  The inverter unit 5 controls the motor unit 4 by generating a magnetic force by passing a current through a coil (not shown) wound around the stator 6.

  Next, the operation of the gas compressor 1 will be described.

  First, a current flows through a coil wound around the stator 6 of the motor unit 4 by the control of the inverter unit 5. When a current flows through the coil, a magnetic force is generated, and the motor rotor 8 disposed on the inner periphery of the stator 6 rotates.

  As the motor rotor 8 rotates, the drive shaft 33 fixed to the motor rotor 8 rotates, and the rotor 29 fixed to the drive shaft 33 also rotates.

  At this time, with the rotation of the rotor 29, the refrigerant flows into the suction chamber 13, and the refrigerant is sucked from the suction chamber 13 into the cylinder chamber 35 through the suction hole 40 of the front side block 25a. The refrigerant sucked into the cylinder chamber 35 is supplied between the vanes 31 and the vanes 31 (closed space), and the closed space is narrowed by further rotation of the rotor 29, and the refrigerant is compressed.

  When the compressed refrigerant reaches a certain pressure or higher, the discharge valve 36 is pushed open and discharged from the discharge hole 34 to the discharge chamber 17 through the discharge hole 38. The refrigerant discharged into the discharge chamber 17 is discharged from a discharge port (not shown) to a refrigeration cycle (not shown).

  Thus, the pressure of the discharge chamber 17 becomes high by compressing the refrigerant by the compression unit 3. As the pressure in the discharge chamber 17 increases, the oil O is supplied from the oil supply hole 57 to the rear side bearing 59 through the rear side oil supply path 67a. Further, high-pressure oil O is supplied from the oil supply hole 57 to the front side bearing 41 through the rear side oil supply path 67 b, the cylinder side oil supply path 37 of the cylinder block 23, and the front side oil supply path 43. The

  The oil O supplied to the front bearing 41 is supplied to the front annular groove 51 and flows into the suction chamber 13 and the intermediate pressure supply groove 47 through the gap between the front bearing 41 and the drive shaft 33. At this time, since the gap between the front bearing 41 and the drive shaft 33 is very small, the pressure between the bearing and the drive shaft 33 is reduced and the pressure is lower than the discharge pressure (high pressure). The oil O having an intermediate pressure higher than the refrigerant suction pressure (low pressure) before flowing into the intermediate pressure supply groove 47.

  The high-pressure oil O supplied to the rear-side annular groove 69 flows through the gap between the rear-side bearing 59 and the drive shaft 33 to the intermediate pressure supply groove 63 side and the discharge chamber 17 side. The oil O that has flowed toward the discharge chamber 17 is supplied to the intermediate pressure supply groove 63 through a through hole (not shown).

  The intermediate pressure oil O supplied to the intermediate pressure supply grooves 47 and 63 communicates with the back pressure space 73 at least in the first half position of the compression chamber 35a, and supplies the intermediate pressure oil O to the back pressure space 73. .

  The oil O supplied to the rear-side annular groove 69 is supplied to the high-pressure supply groove 65 through the communication path 61.

  The high-pressure oil O supplied to the high-pressure supply groove 65 communicates with the back pressure space 73 of the rotor 29 at least in the second half compression position of the compression chamber 35a as the rotor 29 rotates, and the high pressure oil O is supplied to the back pressure space 73. O is supplied. The high-pressure oil O supplied to the back pressure space 73 is supplied to the vane groove 71 and applies a back pressure to the back surface of the vane 31 to cause the vane 31 to protrude from the vane groove 71.

  The high pressure oil O supplied from the high pressure supply groove 65 to the back pressure space 73 supplies the high pressure oil O to the high pressure supply groove 49 through the back pressure space 73.

  For this reason, the same pressure acts on the end surfaces on both sides of the rotor 29, and no offset load acts on the rotor 29.

  Further, since an uneven load does not act on the rotor 29, it is possible to prevent an increase in sliding resistance between the end surface of the rotor 29 and the end surfaces of the pair of side blocks 25 due to the inclination of the rotor 29.

  In addition, since it is possible to prevent the sliding resistance between the rotor 29 and the side block 25 from increasing, it is possible to prevent wear of the side block 25 and to ensure the airtightness of the compression portion 3.

  In the present embodiment, the communication path 61 communicating with the high-pressure supply groove 65 is provided in the rear side block 25b, but a communication path may be provided in the front side block 25a. That is, when providing the communication path in the front side block 25a, the communication path may be provided so that the high-pressure supply groove 49 and the front-side annular groove 51 of the front side block 25a are in communication.

DESCRIPTION OF SYMBOLS 1 Gas compressor 21 Oil reservoir 23 Cylinder block 25 Side block 29 Rotor 31 Vane 35 Cylinder chamber 35a Compression chamber 37, 43, 67a, 67b Oil supply path 39, 53 Both end surfaces 46, 62 Pressure supply groove 47, 63 Intermediate pressure supply Grooves 49, 65 High pressure supply groove 71 Vane groove 73 Back pressure space

Claims (1)

A cylinder chamber (35) is provided in the cylinder block (23) by holding the cylinder block (23) by a pair of side blocks (25).
A rotor (29) that is rotatable in the cylinder chamber (35) and that has an eccentric position of the cylinder chamber (35) as a rotation center is provided,
A plurality of vane grooves (71) opening on the outer peripheral surface of the rotor (29), each provided with a vane (31) so as to be freely projectable;
A compression chamber (35a) is formed by the inner peripheral surface of the cylinder chamber (35) and two adjacent vanes (31) protruding from the vane groove (71).
In the vane groove (71) of the rotor (29), a back pressure space (73) is formed on the back side of the vane (31),
Pressure supply grooves (46, 62) are provided on both end faces (39, 53) of the pair of side blocks (25), and back pressure is supplied to the back pressure space (73) from the pressure supply grooves (46, 62). A gas compressor (1) that
The pressure supply grooves (46, 62) are provided at symmetrical positions on both end faces (39, 53) of the pair of side blocks (25),
Intermediate pressure supply grooves (47, 63) that open to the back pressure space (73) at the first half compression position of the compression chamber (35a) and supply an intermediate pressure lower than the discharge pressure and higher than the suction pressure;
A pair of the side blocks (25) are provided at symmetrical positions on both end faces (39, 53), open to the back pressure space (73) at the second half compression position of the compression chamber (35a), and supply discharge pressure. Consisting of high-pressure supply grooves (49, 65),
The oil O stored in the oil reservoir (21) is supplied to the high-pressure supply groove (49, 65) on one side through the oil supply passage (37, 43, 67a, 67b) and the communication passage (61). ,
Oil O is supplied to the high pressure supply groove (49, 65) on the other side through the back pressure space (73) of the rotor (29) from the high pressure supply groove (49, 65) on the one side. Gas compressor (1).

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