JP5831619B1 - Gas compressor - Google Patents

Abstract

An object of the present invention is to prevent the occurrence of chattering of a vane due to temporary decompression of a back pressure space of the vane in the latter stage of the compression process or in the discharge process. The back pressure space 77 of the vane groove 75 that has finished communicating with the intermediate pressure supply groove 67 is then connected to the first supply section 69a on the upstream side of the high pressure supply groove 69 in the rotational direction X of the rotor 23. The high pressure is supplied from the first supply unit 69a. Thereafter, the back pressure space 77 shifts the communication destination to the second supply unit 69b on the downstream side in the rotation direction X, and receives supply of high pressure from the second supply unit 69b. Then, when the communication destination of the back pressure space 77 is an interval 69c between the first supply part 69a and the second supply part 69b, the inner peripheral surface 33d of the cylinder chamber 33 with which the vane 25 is slidably contacted is used to rotate the rotor 23. The region (c) in which the reduction rate of the protruding stroke of the vane 25 is small is set to prevent the pressure in the back pressure space 77 from temporarily increasing when communicating with the interval 69c. [Selection] Figure 7

Description

  The present invention relates to a so-called vane rotary type gas compressor.

  As shown in Patent Document 1, various gas compressors have been conventionally proposed.

  FIG. 9 shows a compression block arranged in a conventional gas compressor.

  This compression block has a cylinder block 100 and a pair of side blocks 101 disposed on the left and right of the cylinder block 100. A cylinder chamber 105 is formed inside the cylinder block 100 and the pair of side blocks 101. The cylinder block 100 is provided with a suction port 110 and two discharge ports 108.

  A rotor 102 is rotatably disposed in the cylinder chamber 105. A plurality of vane grooves 106 are formed in the rotor 102 at intervals. A vane 103 is disposed in each vane groove 106 so as to be able to appear and retract from the outer peripheral surface of the rotor 102. Back pressure space 107 (107A, 107B, 107C) is formed on the back side of vane groove 106 from vane 103. The back pressure space 107 is open on both side surfaces of the rotor 102.

  An intermediate pressure supply groove 113 and a high pressure supply groove 114 are formed on the rotation trajectory of the back pressure space 107 on the wall surface of each side block 101 on the cylinder chamber 105 side. The intermediate pressure supply groove 113 is supplied with an intermediate pressure that is higher than the sucked refrigerant and lower than the discharged refrigerant. The high pressure supply groove 114 is supplied with a high pressure that is equivalent to the discharged refrigerant.

  In the cylinder chamber 105, compression chambers 105a, 105b, and 105c are formed surrounded by two vanes 103. When the rotor 102 rotates, the compression chambers 105a, 105b, and 105c perform a suction process, a compression process, and a discharge process, and repeat this series of processes.

  In the suction process, the volumes of the compression chambers 105a, 105b, and 105c gradually increase, and the refrigerant is sucked from the suction port 110. In the compression process, the volumes of the compression chambers 105a, 105b, and 105c are gradually reduced to compress the refrigerant. In the discharge process, when the volume of the compression chambers 105a, 105b, and 105c gradually decreases and the refrigerant pressure exceeds a predetermined pressure, the on-off valve 109 is opened and the refrigerant is discharged from the discharge port.

  In such a series of steps, the refrigerant pressure in the compression chambers 105a, 105b, and 105c presses each vane 103 in the direction in which each vane 103 is stored in the vane groove 106 (hereinafter referred to as “storage direction”). The tip of each vane 103 slides on the inner wall of the cylinder chamber 105 by the back pressure acting on the space 107, and the compression chambers 105a, 105b, 105c can reliably compress the refrigerant.

  Here, in the initial stage of the suction process and the compression process where the pressure in the storage direction is small, the intermediate pressure from the intermediate pressure supply groove 113 is applied as the back pressure. Further, in the latter stage of the compression process where the pressure in the storage direction of the vane 103 is large or in the discharge process, the high pressure from the high-pressure supply groove 114 acts as a back pressure. In this way, by changing the back pressure applied to the vane 103 in accordance with the pressure in the storage direction of the vane 103, the sliding resistance of the vane 103 is reduced as much as possible to reduce fuel consumption.

JP 2013-194549 A

  By the way, in the conventional example, when the back pressure space 107 transitions from the intermediate pressure supply groove 113 to the high pressure supply groove 114, the preceding rotation downstream back pressure space 107 is already in communication with the high pressure supply groove 114. Yes. For this reason, when the following back pressure space 107 in the upstream of rotation finishes being transferred to the high pressure supply groove 114, the two back pressure spaces 107 are in communication with the high pressure supply groove 114 simultaneously.

  At this time, as shown in P of FIG. 10, the pressure in the downstream back pressure space 107 communicating with the upstream upstream pressure space 107 having the intermediate pressure via the high pressure supply groove 114 is temporarily higher than the high pressure. Decline. The vane 103 on the downstream side of the rotation is temporarily stored in the vane groove 106 because the refrigerant pressure in the compression chamber 105 in the later stage of the compression process or in the discharge process acts in the storage direction of the vane 103. Chattering may occur.

  The present invention has been made in view of the above circumstances, and an object of the present invention is, for example, to prevent occurrence of chattering of the vane due to temporary decompression of the back pressure space of the vane in the later stage of the compression process or in the discharge process. In carrying out the device, it is to maintain the operation performance as a gas compressor.

In order to achieve the above object, the gas compressor of the present invention described in claim 1
A cylindrical cylinder block having therein a cylinder chamber in which the refrigerant is compressed;
A side block attached to a side portion of the cylinder block and sealing an opening of the cylinder chamber in the side portion;
A rotor that rotates in the cylinder chamber and has a plurality of vane grooves that are open on an outer peripheral surface facing the inner peripheral surface of the cylinder chamber and spaced apart in the rotation direction;
A plurality of vanes that are respectively housed in the respective vane grooves, protrude from and emerge from the outer peripheral surface, slidably contact the inner peripheral surface of the cylinder chamber, and partition the inner peripheral surface and the outer peripheral surface of the rotor into a plurality of compression chambers. When,
It is formed in at least one of the side blocks and communicates with a back pressure space at the groove bottom of the vane groove that houses the vane that partitions the compression chamber from the suction process to the compression process, and the suction process to the compression process. An intermediate pressure supply unit for supplying an intermediate pressure larger than the refrigerant pressure in the compression chamber to the back pressure space;
Communicating after the communication with the intermediate pressure supply section is completed in the back pressure space of the vane groove formed in at least one of the side blocks and housing the vane for partitioning the compression chamber from the compression process to the discharge process. And a high-pressure supply unit that supplies a higher pressure than the refrigerant pressure and the intermediate pressure in the compression chamber from the compression step to the discharge step to the back pressure space,
The high-pressure supply unit is divided into a plurality of independent supply units arranged at intervals in the rotation direction,
The interval is arranged at a position communicating with the back pressure space at a rotational position of the rotor where a reduction rate of the protruding stroke of the vane with respect to the vane groove is a predetermined threshold value or less.
It is characterized by that.

Moreover, the gas compressor of the present invention described in claim 2 is the gas compressor of the present invention described in claim 1,
The inner circumferential surface of the cylinder chamber is
(A) a region in which a projecting stroke of the vane slidingly contacting the inner peripheral surface increases as the rotor rotates in the rotation direction;
(B) a region in which a protruding stroke of the vane slidingly contacting the inner peripheral surface decreases with rotation of the rotor in the rotation direction;
(C) The protrusion stroke from the vane groove of the vane slidably contacting the inner peripheral surface decreases with the rotation of the rotor in the rotation direction, and the reduction rate is smaller than that in the region (b). region,
(D) The projecting stroke of the vane that is in sliding contact with the inner peripheral surface decreases with the rotation of the rotor in the rotational direction, and the reduction rate is larger than that in the region of (c). And an area smaller than the area of (b),
Are formed sequentially in the rotational direction (X),
The interval is arranged at a position communicating with the back pressure space of the vane groove accommodating the vane when the vane is in sliding contact with the area (c) of the inner peripheral surface.
It is characterized by that.

  According to the present invention, the back pressure space of the vane groove that has finished communicating with the intermediate pressure supply unit communicates with the supply unit located on the most upstream side of the high pressure supply unit in the rotation direction of the rotor, and the high pressure from the supply unit Is supplied. Thereafter, the back pressure space ends communication with the supply unit, and communicates with the next supply unit adjacent to the downstream side in the rotation direction.

  When the communication destination of the back pressure space is transferred from the upstream supply part to the downstream supply part of the adjacent high pressure supply part in the rotational direction of the rotor, the back pressure space is always downstream of the upstream supply part and the downstream supply part. A state of communicating with at least one of the supply unit on the side is maintained.

  Moreover, when the back pressure space spans the space between the two supply units when the communication destination of the back pressure space moves from the upstream supply unit to the downstream supply unit of the high pressure supply unit, the back pressure space is overlapped by the overlap. The communication cross-sectional area with respect to each supply part of pressure space reduces, or the communication with respect to each supply part of back pressure space is interrupted | blocked.

  At this time, when the vane immerses into the back pressure space side of the vane groove as the rotor rotates and the volume of the back pressure space decreases, the high pressure in the back pressure space is reduced to the upstream or downstream supply section by the reduced volume. The efficiency of evacuation decreases, or the high pressure in the back pressure space cannot be evacuated to the upstream or downstream supply section. Then, the pressure in the back pressure space temporarily rises in the later stage of the compression process and in the discharge process, and the pressing force of the vane against the inner peripheral surface of the cylinder chamber increases more than necessary, and the sliding resistance between the two increases. There is a possibility.

  On the other hand, in the present invention, when the back pressure space of the vane groove communicates with the space between the two supply parts, the reduction rate of the vane protrusion stroke with respect to the vane groove is predetermined within the inner peripheral surface of the cylinder chamber. The vane slides on the part below the threshold. For this reason, the reduction rate of the volume of the back pressure space when the back pressure space communicates with the interval between the two supply parts is within a range in which the protruding stroke of the vane is reduced at a reduction rate equal to or less than a predetermined threshold value. It is suppressed.

  Therefore, the occurrence of a temporary pressure rise in the back pressure space when the back pressure space of the vane groove communicates with the space between the two supply portions of the high pressure supply portion is suppressed or prevented at a later stage of the compression process or discharge. It is possible to prevent an increase in the sliding resistance of the vane with respect to the inner peripheral surface of the cylinder chamber due to a temporary increase in the back pressure space of the vane in the process. Thereby, it is possible to prevent an increase in power necessary for the rotation of the rotor and to maintain the operation performance as a gas compressor.

It is sectional drawing which shows the whole structure of the vane rotary type gas compressor which concerns on one Embodiment of this invention. It is an AA arrow line view of the gas compressor of FIG. It is a BB arrow line view of the gas compressor of FIG. It is explanatory drawing which expands and shows the principal part of the compression block shown in FIG. It is explanatory drawing which shows the hypothetical example at the time of arrange | positioning the 1st supply part and 2nd supply part of the high voltage | pressure supply groove | channel of FIG. 3 separated by the space | interval which the back pressure space of a vane groove | channel does not communicate in any way. It is a graph which shows the change according to the rotation angle of the rotor of the pressure of the compression chamber of FIG. 5, and the pressure of the back pressure space of the vane of a vane groove | channel. It is explanatory drawing which shows the communication cross-sectional area with the 1st supply part of the high-pressure supply groove of FIG. 3, a 2nd supply part, and the back pressure space of a vane groove. It is a graph which shows the change according to the rotation angle of the rotor of the pressure of the compression chamber of FIG. 3, and the pressure of the back pressure space of the vane of a vane groove | channel. It is explanatory drawing which shows the inside of the compression block of the conventional gas compressor. It is a graph which shows the change according to the rotation angle of the rotor of the pressure of the compression chamber of FIG. 9, and the pressure of the back pressure space of the vane of a vane groove | channel.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings.

  As shown in FIG. 1, a gas compressor 1 according to an embodiment of the present invention transmits a driving force to a substantially cylindrical housing 2, a compression unit 3 accommodated in the housing 2, and the compression unit 3. A motor unit 4 and an inverter unit 5 that is fixed to the housing 2 and controls driving of the motor unit 4 are provided.

  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 compression part 3 is fixed to the inner wall 13 of the rear case 9. The compression unit 3 has a suction chamber 11 formed on one side and a discharge chamber 15 formed on the other side so as to partition the inside of the housing 2. A discharge port (not shown) that connects the discharge chamber 15 and the refrigeration cycle is formed on the outer periphery of the rear case 9. In addition, an oil reservoir 17 in which oil O for maintaining the lubricity of the compression unit 3 is stored is formed below the discharge chamber 15.

  The compression unit 3 protrudes and retracts from the compression block 19 forming the cylinder chamber 33, the oil separator 21 fixed to the compression block 19, the rotor 23 rotatably accommodated in the cylinder chamber 33, and the rotor 23. A vane 25 (see FIG. 3) that partitions the cylinder chamber 33 and a drive shaft 27 that is fixed integrally with the rotor 23 and transmits a driving force are provided.

  The compression block 19 includes a cylinder block 29, a pair of side blocks 31, and a cylinder chamber 33 formed on the inner periphery of the cylinder block 29.

  As shown in FIG. 3, the cylinder block 29 has an elliptical cylinder chamber 33 distorted inside. The opening of the cylinder chamber 33 is closed by holding both ends of the cylinder block 29 by a pair of side blocks 31.

  As shown in FIGS. 3 and 4, the rotor 23 is arranged so that one location is in contact with the inner wall of the cylinder chamber 33, and is arranged with the position shifted from the center (center of gravity) of the cylinder chamber 33 as the rotation center. A vane groove 75 opened on the outer peripheral surface of the rotor 23 and a back pressure space 77 on the back side of the vane 25 are provided.

  The cylinder chamber 33 is partitioned into a plurality in the rotational direction X of the rotor 23 by a plurality of vanes 25 that appear and disappear from the plurality of vane grooves 75 of the rotor 23. Thereby, a plurality of compression chambers 33a, 33b, 33c are formed between the inner peripheral surface 33d of the cylinder chamber 33 and the outer peripheral surface 23a of the rotor 23.

  The cylinder block 29 includes a suction hole 39 for sucking refrigerant into the cylinder chamber 33, a discharge hole 35 for discharging refrigerant compressed in the cylinder chamber 33, an on-off valve 37 for opening and closing the discharge hole 35, and a side block. And a cylinder-side oil supply passage 41 communicating with the 31 oil supply passages.

  As shown in FIG. 1, the pair of side blocks 31 includes a front side block 31a and a rear side block 31b, and an oil separator 21 is fixed to the rear side block 31b.

  The front side block 31a communicates with the front side end face 43 that contacts the cylinder block 29, the suction hole 39, a suction hole (not shown) that sucks refrigerant from the suction chamber 11, and a front side that rotatably supports the drive shaft 27. A bearing 47 and a front side oil supply path 49 communicating with the cylinder side oil supply path 41 are provided.

  The front-side end face 43 is provided with a pressure supply groove, and the pressure supply groove supplies an intermediate pressure (intermediate pressure) higher than the sucked refrigerant and lower than the pressure of the discharged refrigerant to the back pressure space 77. Intermediate pressure supply groove 51 and high pressure supply groove 53 provided at a position facing high pressure supply groove 69 on the rear side block 31b side.

  The front side bearing 47 is formed with an annular front side annular groove 55 and is provided in communication with one end side of the front side oil supply passage 49. The other end side of the front side oil supply passage 49 is in communication with the cylinder side oil supply passage 41.

  As shown in FIG. 2, the rear side block 31 b is configured to freely rotate the rear side end face 57 that contacts the cylinder block 29, the oil supply hole 59 that sucks oil O stored below the discharge chamber 15, and the drive shaft 27. A rear-side bearing 63 to be supported and a rear-side oil supply passage 59b communicating with the cylinder-side oil supply passage 41 are provided.

  The rear-side end surface 57 has a discharge hole 61 for discharging the refrigerant compressed in the cylinder chamber 33, and an intermediate pressure that is higher than the pressure (suction pressure) of the sucked refrigerant and lower than the pressure (discharge pressure) of the discharged refrigerant. An intermediate pressure supply groove 67 for supplying oil to the back pressure space 77 (corresponding to an intermediate pressure supply portion in claims) and high pressure oil that is the pressure of the discharged refrigerant (discharge pressure) are supplied to the back pressure space 77. And a high-pressure supply groove 69 (corresponding to a high-pressure supply part in claims).

  The high-pressure supply groove 69 is divided into a first supply unit 69 a and a second supply unit 69 b that are independent from each other in the rotation direction X of the rotor 23. In the present embodiment, in the rotational direction X of the rotor 23, an interval 69c having a dimension equal to or larger than the back pressure space 77 of the vane groove 75 is provided between the first supply unit 69a and the second supply unit 69b.

  The first supply portion 69a and the second supply portion 69b have high-pressure supply passages 71a and 71b, respectively. One end side of each of the high-pressure supply passages 71a and 71b communicates with the rear-side annular groove 73. The end sides communicate with the first supply unit 69a and the second supply unit 69b, respectively.

  The high-pressure supply groove 53 of the front side block 31a facing the high-pressure supply groove 69 is also divided into two supply parts (not shown) similar to the first supply part 69a and the second supply part 69b.

  The back pressure space 77 (see FIGS. 3 and 4) formed in the rotor 23 communicates with the intermediate pressure supply grooves 51 and 67 in the first half position of compression, and high pressure in the second half position of compression, as the rotor 23 rotates. It communicates with the supply grooves 53 and 69.

  In the state shown in FIG. 4, the compression chamber 33b moved from the suction process to the compression process by the rotation of the rotor 23, and the compression moved from the compression process to the discharge process located downstream of the compression chamber 33b in the rotation direction X of the rotor 23. A back pressure space 77B of the vane groove 75 of the vane 25B partitioning the chamber 33a communicates with the first supply portion 69a of the high pressure supply groove 69. The back pressure space 77B communicates with an interval 69c between the first supply unit 69a and the second supply unit 69b in the rotation direction X of the rotor 23.

  In this state, the back pressure space 77A of the vane groove 75 of the vane 25A that precedes the downstream side of the vane 25B in the rotation direction X of the rotor 23 has already finished communicating with the second supply unit 69a, and is downstream of the rotation direction X. Communication with the intermediate pressure supply unit 67 located on the side begins.

  The first supply unit 69a and the second supply unit 69b both have a back pressure space 77B of the preceding vane 25A and a back pressure space 77B of the next vane 25B following the vane 25A in the rotation direction X of the rotor 23. Are formed in a shape that does not communicate at the same time. This relationship also applies to the back pressure spaces 77B and 77C of the vanes 25B and 25C and the back pressure spaces 77C and 77A of the vanes 25C and 25A moving back and forth in the rotation direction X of the rotor 23.

  The distance between the intermediate pressure supply groove 67 and the first supply part 69a in the rotational direction X of the rotor 23 and the distance between the second supply part 69b and the intermediate pressure supply groove 67 are the first supply part 69a and the second supply part. Similarly to the interval 69c between 69b, it is set wider than the width of the back pressure space 77 in the rotation direction X of the rotor 23.

  As shown in FIG. 1, the oil supply hole 59 is formed in communication with the rear side oil supply path 59a, and is branched from the rear side oil supply path 59a to form a rear side oil supply path 59b. The rear side oil supply path 59 b communicates with the cylinder side oil supply path 41.

  An annular rear side annular groove 73 is formed in the rear side bearing 63 and communicates with the rear side communication path 65. The rear side communication passage 65 has one end communicating with the rear annular groove 73 and the other end opening into the high pressure supply groove 69.

  The oil separator 21 is fixed to the rear side block 31b, and the refrigerant compressed in the cylinder chamber 33 flows into the oil separator 21 to separate the refrigerant from the oil O.

  The drive shaft 27 is fixed to the rotor 23 on one side and is rotatably supported by bearings 47 and 63 of the side blocks 31a and 31b. The motor unit 4 is fixed to the other side of the drive shaft 27.

  The motor unit 4 includes a stator 79 fixed to the inner wall 13 of the rear case 9, and a motor rotor 81 that is rotatably disposed on the inner peripheral side of the stator 79 and rotates by magnetic force. The motor rotor 81 is rotated by the magnetic force, so that the rotational driving force is transmitted to the compression unit 3.

  Here, the position of the gap 69c between the first supply portion 69a and the second supply portion 69b of the high-pressure supply groove 69 in the rotation direction X of the rotor 23 will be described. First, when the communication destination of the back pressure space 77 moves from the first supply portion 69a to the second supply portion 69b, only the gap 69c wider than the back pressure space 77 in the rotation direction X of the rotor 23 and the back pressure space. 77 occurs.

  In this state, when the protrusion stroke of the vane 25 with respect to the vane groove 75 decreases as the rotor 23 rotates in the rotation direction X, the volume of the back pressure space 77 decreases. At this time, since the back pressure space 77 does not communicate with either the first supply unit 69a or the second supply unit 69b, the high pressure corresponding to the reduced volume cannot be retreated.

  Accordingly, the region shown in the range of FIG. 5A on the inner peripheral surface 33d of the cylinder chamber 33, that is, the rate at which the protrusion stroke of the vane 25 with respect to the vane groove 75 is greater than or equal to a certain value as the rotor 23 rotates in the rotation direction X. It is assumed that when the vane 25 is in sliding contact with the region that decreases in step, the interval 69c is arranged at a position where the back pressure space 77 communicates.

  In this case, the volume of the back pressure space 77 is reduced at a rate corresponding to the reduction rate of the protruding stroke of the vane 25 in a state where the back pressure space 77 is blocked from the first supply unit 69a and the second supply unit 69b. As indicated by P1 in FIG. 6, the pressure in the back pressure space 77 temporarily rises.

  When such a pressure increase in the back pressure space 77 occurs, the vane 25 receiving the force in the direction of immersing into the vane groove 75 from the inner peripheral surface 33 d of the cylinder chamber 33 causes the vane 25 to increase the pressure in the back pressure space 77. Trying to protrude from the groove 75. Then, the pressing force of the vane 25 against the inner peripheral surface 33d of the cylinder chamber 33 increases more than necessary, and the sliding resistance between the vane 25 and the inner peripheral surface 33d of the cylinder chamber 33 may increase.

  For this reason, in the gas compressor 1 of this embodiment, the decreasing rate of the protrusion stroke with respect to the vane groove 75 of the vane 25 accompanying the rotation in the rotation direction X of the rotor 23 on the inner peripheral surface 33d of the cylinder chamber 33 is described above. An interval 69c is arranged at a position where the back pressure space 77 is lent when the vane 25 is in sliding contact with an area where the reduction rate of the protruding stroke is small, which is a reduction rate lower than a predetermined rate and less than a predetermined threshold. I tried to do it.

Specifically, in the present embodiment, as shown in FIG.
(A) a region in which the protruding stroke from the vane groove 75 of the vane 25 slidably contacting the inner peripheral surface 33d of the cylinder chamber 33 increases as the rotor 23 rotates in the rotation direction X;
(B) a region in which the protrusion stroke from the vane groove 75 of the vane 25 slidably contacting the inner peripheral surface 33d of the cylinder chamber 33 decreases as the rotor 23 rotates in the rotation direction X;
(C) The protrusion stroke from the vane groove 75 of the vane 23 slidably in contact with the inner peripheral surface 33d of the cylinder chamber 33 decreases with the rotation of the rotor 23 in the rotation direction X, and the rate of decrease is the region (b). Smaller area,
(D) The protrusion stroke from the vane groove 75 of the vane 25 slidably in contact with the inner peripheral surface 33d of the cylinder chamber 33 decreases with the rotation of the rotor 23 in the rotation direction X, and the reduction rate is the region (c). Larger than and smaller than the area of (b),
Are formed so as to be successively continuous in the rotation direction X of the rotor 23.

  Therefore, when the vane 25 is in sliding contact with the region (c) where the reduction rate of the protruding stroke of the vane 25 due to the rotation of the rotor 23 in the rotation direction X is the lowest, the back pressure space 77 is spaced at a position where it communicates. 69c is arranged.

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

  First, a current flows through a coil wound around the stator 79 of the motor unit 4 by the control of the inverter unit 5 shown in FIG. When a current flows through the coil, a magnetic force is generated, and the motor rotor 81 disposed on the inner periphery of the stator 79 rotates.

  As the motor rotor 81 rotates, the drive shaft 27 with the motor rotor 81 fixed to one end side rotates, and the rotor 23 fixed to the other end side drive shaft 27 also rotates.

  As the rotor 23 rotates, the refrigerant flows into the suction chamber 11, and the refrigerant is sucked from the suction chamber 11 into the cylinder chamber 33 through a suction hole (not shown) of the front side block 31a (suction process). The refrigerant sucked into the cylinder chamber 33 forms compression chambers 33a, 33b, 33c in the cylinder chamber 33 by the plurality of vanes 25, and the rotor 23 rotates to compress the refrigerant in the compression chambers 33a, 33b, 33c. (Compression process).

  The refrigerant compressed in the cylinder chamber 33 pushes the opening / closing valve 37 to discharge from the discharge hole 35 (discharge process), and is discharged from the discharge hole 61 to the discharge chamber 15 through the oil separator 21. The refrigerant discharged from the discharge hole 61 is separated into refrigerant and oil O by the oil separator 21, and the refrigerant is discharged from a discharge port (not shown) to a refrigeration cycle (not shown). It is stored in.

  The oil stored below the discharge chamber 15 is supplied from the oil supply hole 59 of the rear side block 31b to the rear side bearing 63 through the rear side oil supply path 59a.

  The high-pressure oil supplied to the rear-side bearing 63 is squeezed between the drive shaft 27 and thereby is higher than the pressure (suction pressure) of the sucked refrigerant and lower than the pressure (discharge pressure) of the discharged refrigerant. The oil O that has become the intermediate pressure is supplied to the intermediate pressure supply groove 67 through the gap between the drive shaft 27 and the rear side block 31b.

  As shown in FIG. 3, the intermediate pressure oil O supplied to the intermediate pressure supply groove 67 supplies intermediate pressure to the back pressure space 77 from the refrigerant suction process to the compression process range, and the vane groove 75 supplies the vane. Intermediate pressure is supplied to the back surface of the vane 25 so that 25 protrudes.

  The high-pressure oil O supplied to the rear-side bearing 63 passes through the first supply portion 69a and the first supply portion 69a of the high-pressure supply groove 69 from the high-pressure supply passages 71a and 71b that open to the rear-side end surface 57 via the rear-side communication passage 65. 2 is supplied to the supply unit 69b.

  The high-pressure oil O supplied to the first supply unit 69a and the second supply unit 69b supplies high pressure to the back pressure space 77 from the refrigerant compression process to the discharge process as shown in FIG. High pressure is supplied to the back surface of the vane 25 so that the vane 25 protrudes from the groove 75. The first supply unit 69 a and the second supply unit 69 b communicate with the corresponding supply units (not shown) of the high pressure supply groove 53 on the front side block 31 a side via the back pressure space 77, and the high pressure supply groove 53. High pressure is also supplied from each supply section to the back pressure space 77.

  The high-pressure oil O flows from the oil supply hole 59 into the rear side oil supply path 59a, branches from the rear side oil supply path 59a, passes through the rear side oil supply path 59b, and passes through the cylinder side oil supply path 41. Then, the oil is supplied from the front oil supply passage 49 to the front bearing 47.

  The high pressure oil O supplied to the front side bearing 47 becomes an intermediate pressure by being squeezed between the drive shaft 27, and the oil O which has become the intermediate pressure is a gap between the drive shaft 27 and the front side block 31a. And is supplied to the intermediate pressure supply groove 51.

  The high-pressure oil O supplied from the high-pressure supply grooves 53 and 69 of the front side block 31a and the rear side block 31b is supplied to the back pressure space 77 of the rotor 23 at the second half rotation position of the rotor 23, and passes through the vane 25 from the vane groove 75. The back pressure to make it protrude is given.

  According to the gas compressor 1 of the present embodiment, the back pressure space 77 of the vane groove 75 that has finished communicating with the intermediate pressure supply groove 67 communicates with the first supply part 69a of the high pressure supply groove 69, and the first supply part High pressure is supplied from 69a.

  Thereafter, the back pressure space 77 communicates with the first supply unit 69a before the back pressure space 77 of the next vane groove 75 located on the upstream side in the rotation direction X communicates with the first supply unit 69a. After that, the high pressure is supplied again by communicating with the second supply unit 69b located on the downstream side in the rotation direction X independent of the first supply unit 69a.

  Therefore, when the back pressure space 77 that has finished communicating with the intermediate pressure supply groove 67 communicates with the first supply portion 69 a of the high pressure supply groove 69, the back pressure space 77 is adjacent to the downstream side in the rotation direction X. The preceding back pressure space 77 does not communicate with the first supply unit 69a at the same time.

  By preventing the two back pressure spaces 77 from communicating with the first supply unit 69a at the same time, the pressure in the preceding back pressure space 77 is temporarily increased by the intermediate pressure before the pressure increases to the high pressure in the following back pressure space 77 that follows. Can be prevented from being lowered from high pressure. Thereby, it is possible to prevent the occurrence of chattering in which the vane 25 repeatedly contacts and separates from the inner peripheral surface 33d of the cylinder chamber 33 due to temporary pressure reduction of the back pressure space 77 of the vane 25 in the first half of the compression process.

  Further, the back pressure space 77 ends the communication with the second supply unit 69b before the back pressure space 77 of the next vane groove 75 located on the upstream side in the rotation direction X communicates with the second supply unit 69b. . Therefore, when the back pressure space 77 that has finished communicating with the first supply portion 69 a of the high pressure supply groove 69 communicates with the second supply portion 69 b of the high pressure supply groove 69, the back pressure space 77 in the rotational direction X The preceding back pressure space 77 adjacent to the downstream side does not communicate with the second supply unit 69b at the same time.

  By preventing the two back pressure spaces 77 from communicating with the second supply unit 69b at the same time, as indicated by P in the graph of FIG. 10, the pressure of the preceding back pressure space 77 follows the next back. As shown in the graph of FIG. 8, it is possible to prevent the pressure space 77 from being temporarily lowered from the high pressure by the pressure on the way from the intermediate pressure to the high pressure. This prevents chattering that the vane 25 repeatedly contacts and separates from the inner peripheral surface 33d of the cylinder chamber 33 due to temporary pressure reduction of the back pressure space 77 of the vane 25 in the later stage of the compression process or in the discharge process. it can.

  Furthermore, according to the gas compressor 1 of the present embodiment, when the communication destination of the back pressure space 77 is the distance 69c between the first supply portion 69a and the second supply portion 69b, the vane groove of the back pressure space 77 The first supply portion 69a and the second supply portion 69a are slidably in contact with the region (c) in which the reduction rate of the protruding stroke of the vane 25 accompanying the rotation of the rotor 23 in the rotation direction X is the lowest. An interval 69c with the supply unit 69b was positioned.

  For this reason, when the back pressure space 77 communicates with the space 69c between the first supply part 69a and the second supply part 69b, the protruding stroke of the vane 25 is almost reduced as in the part surrounded by the round frame in FIG. In addition, the volume of the back pressure space 77 is hardly reduced. For this reason, as shown in FIG. 8, when the back pressure space 77 communicates with the space 69c, a temporary pressure increase in the back pressure space 77 does not occur.

  Therefore, as indicated by P1 in the graph of FIG. 6, when the communication destination of the back pressure space 77 is the distance 69c between the first supply portion 69a and the second supply portion 69b, the high pressure in the back pressure space 77 As shown in the graph of FIG. 8, it is possible to prevent the retreat path from disappearing and the pressure in the back pressure space 77 from temporarily rising.

  As a result, it is possible to prevent the pressing force of the vane 25 against the inner peripheral surface 33d of the cylinder chamber 33 from being increased more than necessary due to a temporary pressure increase in the back pressure space 77, and the sliding resistance between the two increases. The Therefore, the sliding pressure of the vane 25 with respect to the inner peripheral surface 33d of the cylinder chamber 33 increases due to the temporary pressure increase in the back pressure space 77 in the later stage of the compression process or in the discharge process, and the power necessary for the rotation of the rotor 23 increases. And the operation performance as the gas compressor 1 can be maintained.

  The second supply portion 69b of the high-pressure supply groove 69 has a shape as large as possible in the rotational direction X as long as two back pressure spaces 77 adjacent to each other in the rotational direction X of the rotor 23 do not communicate with each other. It is desirable. By doing so, the back pressure space 77 in which the pressure is increased from the intermediate pressure toward the high pressure by communication with the first supply unit 69a is changed from the early stage of the compression process of the compression chambers 33a, 33b, 33c to the second supply unit. It is possible to stabilize the high pressure by communicating with 69b.

  Thereby, the discharge process of the compression chambers 33a, 33b, and 33c can be started at an early stage, and the on-off valve 37 of the discharge hole 35 is opened at an early stage, so that the high-pressure refrigerant in the compression chambers 33a, 33b, and 33c. Can be efficiently and sufficiently discharged, and the refrigerant compression efficiency can be improved.

  In the present embodiment, the back pressure space 77A of the vanes 25A and 25B (25B, 25C, 25C, and 25A) adjacent to each other in the rotation direction X of the rotor 23 is used for both the first supply unit 69a and the second supply unit 69b. , 77B (77B, 77C, 77C, 77A) do not communicate at the same time. However, one or both of the first supply unit 69a and the second supply unit 69b are connected to the back pressure spaces 77A and 77B (77B) of the two vanes 25A and 25B (25B, 25C, 25C and 25A) adjacent in the rotation direction X. , 77C, 77C, 77A) can be formed in any shape that does not communicate with each other at the same time.

  Further, the distance 69 c between the first supply unit 69 a and the second supply unit 69 b may be smaller than the back pressure space 77 in the rotation direction X of the rotor 23. Even in this case, when the back pressure space 77 straddles the interval 69c when the communication destination of the back pressure space 77 is shifted from the first supply unit 69a of the high pressure supply unit 69 to the second supply unit 69b, the back pressure space 77 overlaps the interval 69c. The communication cross-sectional area with respect to each supply part 69a, 69b of the back pressure space 77 decreases by the amount.

  At this time, when the vane 25 is immersed in the back pressure space 77 side of the vane groove 75 with the rotation of the rotor 23 and the volume of the back pressure space 77 is reduced, the high pressure in the back pressure space 77 is first supplied by the reduced volume. The efficiency of retreating to the part 69a and the second supply part 69b is lowered. Then, the pressure in the back pressure space 77 temporarily rises in the later stage of the compression process and in the discharge process, and the force with which the vane 25 presses the inner peripheral surface 33d of the cylinder chamber 33 increases more than necessary, and the vane 25 and the cylinder chamber are increased. The sliding resistance with the inner peripheral surface 33d of 33 may increase.

  However, when the vane 25 is in sliding contact with the region (c) where the reduction rate of the protruding stroke of the vane 25 due to the rotation of the rotor 23 in the rotational direction X is the lowest, the back pressure space 77 is spaced at a position where it communicates. By disposing 69c, it is possible to prevent the pressure in the back pressure space 77 from temporarily increasing due to a decrease in efficiency of retreating the high pressure in the back pressure space 77. Therefore, the sliding resistance of the vane 25 with respect to the inner peripheral surface 33d of the cylinder chamber 33 increases due to the temporary pressure increase in the back pressure space 77 in the later stage of the compression process or in the discharge process, and the power necessary for the rotation of the rotor 23 increases. And the operation performance as the gas compressor 1 can be maintained.

  When the area of the inner peripheral surface 33d of the cylinder chamber 33 that the vane 25 is in sliding contact with when the back pressure space 77 communicates with the interval 69c is determined based on the reduction rate of the projecting stroke of the vane 25 with respect to the vane groove 75. Determines the upper limit value of the allowable range of the reduction rate of the protruding stroke of the vane 25 with respect to the vane groove 75 according to the allowable range for the temporary increase in the pressure of the back pressure space 77.

  The determined upper limit value is set as a predetermined threshold value, and the vane 25 is in sliding contact with an area on the inner peripheral surface 33d of the cylinder chamber 33 where the reduction rate of the protruding stroke of the vane 25 is equal to or less than this threshold value. The distance 69c may be arranged so that the back pressure space 77 communicates with the space 69c.

  By doing so, the back pressure space 77 is temporarily increased due to a decrease in the protruding stroke of the vane 25 when the back pressure space 77 communicates with the gap 69c between the first supply portion 69a and the second supply portion 69b. Can be within the allowable range. Therefore, the sliding resistance of the vane 25 with respect to the inner peripheral surface 33d of the cylinder chamber 33 increases due to the temporary pressure increase in the back pressure space 77 in the later stage of the compression process or in the discharge process, and the power necessary for the rotation of the rotor 23 increases. And the operation performance as the gas compressor 1 can be maintained.

  In the present embodiment, the high-pressure supply groove 69 is divided into two independent first supply parts 69a and second supply parts 69b in the rotation direction X. However, the present invention is also applicable when the high-pressure supply groove 69 is divided into three or more supply parts in the rotation direction X. In that case, the relationship of the present invention is applied to the relative position between the interval between two supply parts adjacent in the rotation direction X and the inner peripheral surface of the cylinder chamber.

  Further, in the present embodiment, in order to prevent the back pressure space 77 of the vane 25 from communicating with the same supply unit as the back pressure space 77 of the upstream vane 25, the high pressure supply groove 69 in the rotation direction X is the first. The case where the supply unit 69a and the second supply unit 69b are divided has been described as an example. However, the present invention can be widely applied to a gas compressor that divides the high-pressure supply groove 69 into a plurality of parts in the rotation direction X for some reason.

DESCRIPTION OF SYMBOLS 1 Gas compressor 2 Housing 3 Compression part 4 Motor part 5 Inverter part 7 Front head 9 Rear case 11 Suction chamber 13 Inner wall 15,108 Discharge chamber 19 Compression block 21 Oil separator 23,102 Rotor 23a Outer peripheral surface 25 (25A, 25B) , 25C), 103 vane 27 drive shaft 29, 100 cylinder block 31, 101 side block 31a front side block 31b rear side block 33, 105 cylinder chamber 33a, 33b, 33c, 105a, 105b, 105c compression chamber 33d inner peripheral surface 35 discharge Hole 37, 109 On-off valve 39 Suction hole 41 Cylinder side oil supply path 43 Front side end face 47 Front side bearing 49 Front side oil supply path 51, 113 Intermediate pressure supply groove 53, 114 High pressure supply groove 55 Front side annular groove 57 Rear Side end face 59 Oil supply hole 59a Rear side oil supply path 59b Rear side oil supply path 61 Discharge hole 63 Rear side bearing 65 Rear side communication path 67 Intermediate pressure supply groove (intermediate pressure supply section)
69 High pressure supply groove (High pressure supply section)
69a 1st supply part (supply part)
69b 2nd supply part (supply part)
69c Interval 71a, 71b High pressure supply passage 73 Rear side annular groove 75, 106 Vane groove 77 (77A, 77B, 77C), 107 Back pressure space 79 Stator 81 Motor rotor 110 Suction port O Oil X Rotation direction

Claims (2)

A cylindrical cylinder block (29) having therein a cylinder chamber (33) in which the refrigerant is compressed;
Side blocks (31a, 31b) attached to the side of the cylinder block (29) and sealing the opening of the cylinder chamber (33) in the side;
A plurality of vane grooves (75) that rotate in the cylinder chamber (33) and open to the outer peripheral surface (23a) facing the inner peripheral surface (33d) of the cylinder chamber (33) are spaced apart in the rotational direction (X). A rotor (23) having a plurality of
The vane grooves (75) are housed in the respective outer circumferential surfaces (23a) so as to slide in and come into sliding contact with the inner circumferential surface (33d) of the cylinder chamber (33), and the inner circumferential surface (33d) and the rotor ( 23) a plurality of vanes (25) that divide between the outer peripheral surface (23a) and a plurality of compression chambers (33a, 33b, 33c);
Groove of the vane groove (75) which is formed in at least one of the side blocks (31a, 31b) and accommodates the vane (25) which partitions the compression chamber (33a, 33b, 33c) from the suction process to the compression process. An intermediate pressure that communicates with the back pressure space (77) at the bottom and supplies an intermediate pressure larger than the refrigerant pressure in the compression chambers (33a, 33b, 33c) from the suction process to the compression process to the back pressure space (77). A supply section (67);
The vane groove (75) formed in at least one of the side blocks (31a, 31b) and containing the vane (25) partitioning the compression chamber (33a, 33b, 33c) from the compression process to the discharge process. The refrigerant pressure in the compression chambers (33a, 33b, 33c) from the compression process to the discharge process and the intermediate are communicated with the back pressure space (77) after the communication with the intermediate pressure supply unit (67) is completed. A high pressure supply part (69) for supplying a high pressure larger than the pressure to the back pressure space (77),
The high-pressure supply part (69) is divided into a plurality of mutually independent supply parts (69a, 69b) arranged at intervals (69c) in the rotational direction (X),
The interval (69c) is determined by the back pressure space (77) at the rotational position of the rotor (23) where the reduction rate of the protruding stroke of the vane (25) with respect to the vane groove (75) is equal to or less than a predetermined threshold value. ) To communicate with
The gas compressor (1) characterized by the above-mentioned. The inner peripheral surface (33d) of the cylinder chamber (33)
(A) The protrusion stroke from the vane groove (75) of the vane (25) slidably contacting the inner peripheral surface (33d) increases as the rotor (23) rotates in the rotational direction (X). Region (33e),
(B) The protrusion stroke from the vane groove (75) of the vane (25) slidingly contacting the inner peripheral surface (33d) decreases as the rotor (23) rotates in the rotational direction (X). Region (33f),
(C) The protrusion stroke from the vane groove (75) of the vane (25) slidably contacting the inner peripheral surface (33d) decreases as the rotor (23) rotates in the rotational direction (X). A region (33g) whose rate of decrease is smaller than the region of (b), and
(D) The protrusion stroke from the vane groove (75) of the vane (25) slidably contacting the inner peripheral surface (33d) decreases as the rotor (23) rotates in the rotational direction (X). , A region (33f) whose reduction rate is larger than the region (c) and smaller than the region (b),
Are formed sequentially in the rotational direction (X),
The gap (69c) is defined by the vane groove (25) containing the vane (25) when the vane (25) is in sliding contact with the region (33g) of (c) on the inner peripheral surface (33d). 75) is arranged at a position communicating with the back pressure space (77).
The gas compressor (1) according to claim 1, characterized by that.

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