Patent Application
20170350391
The present invention relates to a so-called vane rotary-type gas compressor.
Conventionally, various gas compressors have been proposed as indicated in Patent Literature 1.
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 in the cylinder block 100 and the pair of the 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. The rotor 102 is formed with a plurality of vane grooves 106 at intervals. A vane 103 is disposed in each vane groove 106 so as to freely retractable from an outer peripheral surface of the rotor 102. A back pressure space 107 (107A, 107B and 107C) is formed in the vane groove 106 on the back surface side of the vane 103. The back pressure space 107 opens to both side surfaces of the rotor 102.
An intermediate-pressure supply groove 113 and a high-pressure supply groove 114 are formed in a wall surface on the cylinder chamber 105 side of each side block 101, on a rotation locus of the back pressure space 107. An intermediate pressure that is a pressure higher than that of a sucked refrigerant and is lower than that of the discharged refrigerant is supplied to the intermediate-pressure supply groove 113. High pressure that is a pressure equivalent to that of the discharged refrigerant is supplied to the high-pressure supply groove 114.
Compression chambers 105a, 105b and 105c are formed in the cylinder chamber 105 by being surrounded by the two vanes 103. The compression chambers 105a, 105b and 105c perform a suction process, a compression process and a discharged process and repeat this series of the processes, at the time of rotation of the rotor 102.
In the suction process, the refrigerant is sucked from the suction port 110 by gradual increase in volumes of the compression chambers 105a, 105b and 105c. In the compression process, the refrigerant is compressed by gradual decrease in volumes of the compression chambers 105a, 105b and 105c. In the discharged process, when the volumes of the compression chambers 105a, 105b and 105c are gradually decreased and a refrigerant pressure becomes at least a predetermined pressure, an open/close valve 109 opens and the refrigerant is discharged from the discharge port 108.
In such a series of processes, as to each of the vane 103, although the refrigerant pressures in the compression chambers 105a, 105b and 105c press each of the vanes 103 in a direction (hereinafter, a “storage direction”) in which each of the vane 103 is stored in the vane groove 106, a tip of each of the vane 103 slides along an inner wall of the cylinder chamber 105 by a back pressure acting on the back pressure space 107 and thereby the compression chambers 105a, 105b and 105c are able to reliably compress the refrigerant.
Here, in the suction process and in an early stage of the compression process in which pressure in the storage direction is small, an intermediate pressure from the intermediate-pressure supply groove 113 is made to act as the back pressure. In addition, in a later stage of the compression process and in the discharged process in which the pressure in the storage direction of the vane 103 is large, high pressure from the high-pressure supply groove 114 is made to act as the back pressure. In this way, a sliding resistance of the vane 103 is made as small as possible so as to achieve low fuel consumption by changing the back pressure made to act on the vane 103, in accordance with the pressure in the storage direction of the vane 103.
Patent Literature 1: Japanese Patent Laid-Open Publication No. 2013-194549
In the example shown in
Since the pressure P107B in the rotation upstream back pressure space 107B is intermediate pressure, the pressure P107A in the rotation downstream back pressure space 107A that communicates with the rotation upstream back pressure space 107B via the high-pressure supply groove 114 becomes temporarily lower than a pressure to be supplied to the high-pressure supply groove 114 as shown by P in
The present invention has been made in view of the above-mentioned circumstances and an object of the present invention is to prevent occurrence of chattering of the vane by a temporary reduction in pressure in the back pressure space of the vane, for example, in the later stage of the compression process and in the discharged process, and to maintain operating performance as a gas compressor.
In order to achieve the above-mentioned object, a gas compressor of the present invention includes:
a tubular cylinder block having therein a cylinder chamber in which a refrigerant is compressed;
side blocks that are attached to side parts of the cylinder block and seal an opening of the cylinder chamber on the side parts;
a rotor that rotates in the cylinder chamber and has a plurality of vane grooves opening to an outer peripheral surface facing an inner peripheral surface of the cylinder chamber at intervals in a rotation direction;
a plurality of vanes that is respectively stored in the respective vane grooves, protrudes and retracts from the outer peripheral surface, comes into sliding contact with the inner peripheral surface of the cylinder chamber, and partitions a space between the inner peripheral surface and the outer peripheral surface of the rotor into a plurality of compression chambers;
an intermediate-pressure supply section that is formed in at least one of the side blocks, communicates with a back pressure space at a groove bottom of each of the vane grooves storing the vanes for partitioning the compression chambers from a suction process to a compression process, and supplies, to the back pressure space, an intermediate pressure larger than a refrigerant pressure in each of the compression chambers from the suction process to the compression process; and
a high-pressure supply section that is formed in at least one of the side blocks, communicates with the back pressure space in each of the vane grooves storing the vanes for partitioning the compression chambers from the compression process to a discharged process after communication with the intermediate-pressure supply section has been completed, and supplies, to the back pressure space, high pressure larger than the refrigerant pressure in each of the compression chambers from the compression process to the discharged process and larger than the intermediate pressure, wherein
the high-pressure supply section is divided into a plurality of mutually independent supply sections in the rotation direction,
the second supply section that is positioned at least secondarily from the most upstream side in the rotation direction is formed into a shape in which the second supply section, while communicating with the back pressure space of one vane groove, does not simultaneously communicate with the back pressure space of the other vane groove adjacent to the vane groove on the upstream side in the rotation direction, and the high-pressure supply section is formed in a range in which it simultaneously communicates with the back pressure space of the one vane groove and the back pressure space of the other vane groove adjacent to the vane groove on the upstream side in the rotation direction.
The first embodiment of the present invention will be described with reference to
As shown in
The housing 2 is configured by a front head 7 in which a not shown suction port is formed and a bottomed cylindrical rear case 9 whose opening is closed by the front head 7.
The compression section 3 is fixed to an inner wall 13 of the rear case 9. The compression section 3 is formed with a suction chamber 11 on one side and is formed with a discharge chamber 15 on the other side so as to partition the inside of the housing 2. In addition, a not shown discharge port which communicates the discharge chamber 15 with a refrigerating cycle is formed in an outer periphery of the rear case 9. Additionally, an oil sump 17 which stores an oil O for maintaining lubricity of the compression section 3 is formed under the discharge chamber 15.
The compression section 3 includes a compression block 19 that forms a cylinder chamber 33, an oil separator 21 fixed to the compression block 19, a rotor 23 that is rotatably stored in the cylinder chamber 33, a vane 25 (refer to
The compression block 19 is configured by a cylinder block 29, a pair of side blocks 31, and the cylinder chamber 33 formed on an inner periphery of the cylinder block 29.
As shown in
As shown in
The cylinder chamber 33 is partitioned into a plurality of pieces in a rotation direction X of the rotor 23 by the plurality of vanes 25 that protrudes and retracts from the plurality of vane grooves 75 in the rotor 23. Thereby, a plurality of compression chambers 33a, 33b and 33c is formed between an inner peripheral surface 33d of the cylinder chamber 33 and an outer peripheral surface 23a of the rotor 23.
In addition, the cylinder block 29 is provided with a suction slot 39 through which the refrigerant is sucked into the cylinder chamber 33, a discharge slot 35 through which the refrigerant having been compressed in the cylinder chamber 33 is discharged, an open/close valve 37 which opens/closes the discharge slot 35 and a cylinder-side oil supply path 41 which communicates with an oil supply path of the side block 31.
As shown in
The front-side block 31a is provided with a front-side end surface 43 that abuts on the cylinder block 29, a not shown suction slot that communicates with the suction slot 39 and sucks the refrigerant from the suction chamber 11, a front-side bearing 47 that rotatably supports the drive shaft 27 and a front-side oil supply path 49 that communicates with the cylinder-side oil supply path 41.
The front-side end surface 43 is provided with a pressure supply groove, and the pressure supply groove includes an intermediate-pressure supply groove 51 that supplies, to the back pressure space 77, an intermediate pressure (a middle pressure) higher than that of the sucked refrigerant and lower than that of the discharged refrigerant and a high-pressure supply groove 53 that is provided at a position facing a high-pressure supply groove 69 on the rear-side block 31b side.
In addition, the front-side bearing 47 is formed with an annular front-side annular groove 55, which is provided in communication with the one-end side of the front-side oil supply path 49. Note that the other-end side of the front-side oil supply path 49 is in communication with the cylinder-side oil supply path 41.
As shown in
The rear-side end surface 57 includes a discharge hole 61 through which the refrigerant having been compressed in the cylinder chamber 33 is discharged, an intermediate-pressure supply groove 67 (corresponding to an intermediate-pressure supply section in the claims) which supplies, to the back pressure space 77, the oil of intermediate pressure higher than pressure (suction pressure) of the sucked refrigerant and lower than pressure (discharged pressure) of the discharged refrigerant, and the high-pressure supply groove 69 (corresponding to a high-pressure supply section in the claims) which supplies, to the back pressure space 77, the oil of high pressure that is the pressure (the discharge pressure) of the discharged refrigerant.
The high-pressure supply groove 69 is divided into mutually independent first supply section 69a (corresponding to an upstream-side supply section) and second supply section 69b (corresponding to a downstream-side supply section) in the rotation direction X of the rotor 23.
In addition, high-pressure supply paths 71a and 71b respectively open to the first supply section 69a and the second supply section 69b, and the respective high-pressure supply paths 71a and 71b are in communication with a rear-side annular groove 73 on their one-end sides and are in communication with the first supply section 69a and the second supply section 69b, respectively, on their other-end sides.
Note that 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 sections (not shown) which are similar to the first supply section 69a and the second supply section 69b.
The back pressure space 77 (refer to
In a state shown in
In this state, a back pressure space 77A of the vane groove 75 in a vane 25A that precedes the vane 25B in the downstream side of the vane 25B in the rotation direction X of the rotor 23 has already completed communication with the first supply section 69a and is in communication with the second supply section 69b positioned on the downstream side in the rotation direction X.
In addition, in the rotation direction X of the rotor 23, the first supply section 69a is formed into a shape in which the back pressure space 77A of the preceding vane 25A and the back pressure space 77B of the next vane 25B that follows the vane 25A do not communicate with the first supply section 69a simultaneously. Namely, in the rotation direction X of the rotor 23, the first supply section is formed such that an angle range in which the first supply section 69a extends becomes smaller than a difference between the angle at which the back pressure space 77A is positioned and the angle at which the back pressure space 77B is positioned. In short, a distance between the back pressure space 77A and the back pressure space 77B in the rotation direction X of the rotor 23 is set larger than a width of the first supply section 69a.
In a similar way, in the rotation direction X of the rotor 23, the second supply section 69b is formed into a shape in which the back pressure space 77A of the preceding vane 25A and the back pressure space 77B of the next vane 25B that follows the vane 25A do not communicate with the second supply section 69b simultaneously. Namely, in the rotation direction X of the rotor 23, the second supply section is formed such that an angle range in which the second supply section 69b extends becomes smaller than the difference between the angle at which the back pressure space 77A is positioned and the angle at which the back pressure space 77B is positioned. In short, the distance between the back pressure space 77A and the back pressure space 77B in the rotation direction X of the rotor 23 is set larger than a width of the second supply section 69b.
As described above, restrictions are caused on the angle range in which the first supply section 69a extends and the angle range in which the second supply section 69b extends, on the basis of the difference between the angle at which the back pressure space 77A is positioned and the angle at which the back pressure space 77B is positioned.
Similarly, restrictions are caused on the angle range in which the first supply section 69a extends and the angle range in which the second supply section 69b extends, on the basis of a difference between the angle at which the back pressure space 77B is positioned and an angle at which a back pressure space 77C is positioned.
Likewise, restrictions are caused on the angle range in which the first supply section 69a extends and the angle range in which the second supply section 69b extends, on the basis of a difference between the angle at which the back pressure space 77C is positioned and the angle at which the back pressure space 77A is positioned.
In this way, the shapes of the first supply section 69a and the second supply section 69b are determined on the basis of the angle at which the back pressure space 77 is positioned in the rotation direction X of the rotor 23.
Note that a distance between the intermediate-pressure supply groove 67 and the first supply section 69a and a distance between the second supply section 69b and the intermediate-pressure supply groove 67 in the rotation direction X of the rotor 23 are set larger than a width of the back pressure space 77 in the rotation direction X of the rotor 23.
As shown in
The rear-side bearing 63 is formed with the annular rear-side annular groove 73, which is in communication with a rear-side communication path 65. The rear-side communication path 65 is in communication with the rear-side annular groove 73 on its one-end side and opens to the high-pressure supply groove 69 on its other-end side.
The oil separator 21 is fixed to the rear-side block 31b, the refrigerant having been compressed in the cylinder chamber 33 flows into the oil separator 21, and the refrigerant and the oil O are separated from each other therein.
The drive shaft 27 is fixed to the rotor 23 on its one side and is rotatably supported by the bearings 47 and 63 of the respective side blocks 31a and 31b. In addition, the motor section 4 is fixed to the other side of the drive shaft 27.
The motor section 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 periphery side of the stator 79 and rotates by a magnetic force. The motor rotor 81 transmits a rotational drive force to the compression section 3, due to the rotation by the magnetic force.
Here, there will be described an interval between the first supply section 69a and the second supply section 69b of the high-pressure supply groove 69 in the rotation direction X of the rotor 23.
In the present embodiment, as shown in
Here, as shown in
Since the interval between the first supply section 69a and the second supply section 69b of the high-pressure supply groove 69 in the rotation direction X of the rotor 23 is larger than the width of the back pressure space 77B, there is generated a state where the back pressure space 77B does not communicate with any of the first supply section 69a and the second supply section 69b when a communication destination of the back pressure space 77B shifts from the first supply section 69a to the second supply section 69b.
At this time, the vane 25B stored in the vane groove 75, the back pressure space 77B of which is positioned between the first supply section 69a and the second supply section 69b, receives force acting in a direction of intruding into the vane groove 75 from the inner peripheral surface 33d of the cylinder chamber 33 since the compression chambers 33a and 33b partitioned by the vane 25B stay from the later stage of the compression process to the discharged process. Namely, when the back pressure space 77B is positioned between the first supply section 69a and the second supply section 69b, the volume of the back pressure space 77B is in a state of being reduced.
However, since the back pressure space 77B does not communicate with any of the first supply section 69a and the second supply section 69b at this position, it is not possible to release the high pressure of the amount corresponding to the reduced volume of the back pressure space 77B to any place other than the back pressure space 77B. Accordingly, in the middle stage of shifting the communication destination of the back pressure space 77B from the first supply section 69a to the second supply section 69b, the pressure in the back pressure space 77 temporarily rises as shown by P1 in
When such a pressure rise in the back pressure space 77B is generated, the vane 25B which is receiving force of the direction of intruding into the vane groove 75 from the inner peripheral surface 33d of the cylinder chamber 33 attempts to project from the vane groove 75 by the risen pressure in the back pressure space 77B. Then, there is a possibility that pressing force of the vane 25B against the inner peripheral surface 33d of the cylinder chamber 33 may be increased more than necessary and the sliding resistance between the vane 25B and the inner peripheral surface 33d of the cylinder chamber 33 may be increased.
The similar phenomenon to the above can be generated in a state where the vane 25A and a vane 25C are not in communication with any of the first supply section 69a and the second supply section 69b.
Accordingly, in the gas compressor 1 of the present embodiment, as shown in
Specifically, when the back pressure space 77 is in communication with the first supply section 69a and the second supply section 69b, it is possible to release the high pressure in the back pressure space 77 to the high-pressure supply paths 71a and 71b through which the high pressure oil O is supplied to the first supply section 69a and the second supply section 69b, and the rear-side communication path 65 continued to the high-pressure supply paths 71a and 71b, the rear-side annular groove 73, the rear-side oil supply path 59a, and the oil supply hole 59.
In order to ensure a high-pressure release route which is equal to or better than the above, in the gas compressor 1 of the present embodiment, an interval at which the total of the above-mentioned communication cross-sectional areas Si and S3 becomes at least a minimum path cross-sectional area in a high-pressure oil O supply route for the first supply section 69a and the second supply section 69b, from the high-pressure supply paths 71a and 71b down to the oil supply hole 59, is provided between the first supply section 69a and the second supply section 69b in the rotation direction X of the rotor 23.
Next, an operation of the gas compressor 1 according to the present embodiment will be described.
First, an electric current flows through a coil having been wound on the stator 79 of the motor section 4 by control of the inverter section 5 shown in
The drive shaft 27 on the one-end side of which the motor rotor 81 is fixed rotates by rotation of the motor rotor 81, and also the rotor 23 which is fixed on the other-end side of the drive shaft 27 rotates.
The refrigerant flows into the suction chamber 11 together with rotation of the rotor 23, and the refrigerant is sucked into the cylinder chamber 33 from the suction chamber 11 via a suction slot (not shown) of the front-side block 31a (the suction process). The refrigerant having been sucked into the cylinder chamber 33 enters the compression chambers 33a, 33b and 33c formed in the cylinder chamber 33 by the plurality of vanes 25, and thereby the refrigerant in the compression chambers 33a, 33b and 33c is compressed by rotation of the rotor 23 (the compression process).
The refrigerant having been compressed in the cylinder chamber 33 pushes the open/close valve 37 open, and is discharged from the discharge slot 35 (the discharged process) and is discharged from the discharge hole 61 into the discharge chamber 15 via the oil separator 21. In addition, the refrigerant having been discharged from the discharge hole 61 is separated into the refrigerant and the oil O by the oil separator 21, the refrigerant is discharged from a not shown discharge port to the not shown refrigerating cycle, and the oil O is stored under the discharge chamber 15.
The oil having been stored under the discharge chamber 15 is supplied from the oil supply hole 59 in the rear-side block 31b to the rear-side bearing 63 through the rear-side oil supply path 59a.
The high-pressure oil having been supplied to the rear-side bearing 63 is reduced to intermediate pressure higher than the pressure (the suction pressure) of the sucked refrigerant and lower than the pressure (the discharged pressure) of the discharged refrigerant, by being squeezed between the rear-side bearing 63 and the drive shaft 27, and the oil O having been reduced to the intermediate pressure is supplied to the intermediate-pressure supply groove 67 through a gap between the drive shaft 27 and the rear-side block 31b.
The intermediate pressure oil O having been supplied to the intermediate-pressure supply groove 67 supplies the intermediate pressure to the back pressure space 77 and supplies the intermediate pressure to the back surface of the vane 25 such that the vane 25 projects from the vane groove 75, over a range from the refrigerant suction process to the compression process as shown in
In addition, the high-pressure oil O having been supplied to the rear-side bearing 63 is supplied from the high-pressure supply paths 71a and 71b opening to the rear-side end surface 57 to the first supply section 69a and the second supply section 69b of the high-pressure supply groove 69, via the rear-side communication path 65.
The high-pressure oil O having been supplied to the first supply section 69a and the second supply section 69b supplies the high pressure to the back pressure space 77 and supplies the high pressure to the back surface of the vane 25 such that the vane 25 projects from the vane groove 75, over a range from the refrigerant compression process to the discharged process as shown in
Furthermore, the high-pressure oil O flows into the rear-side oil supply path 59a from the oil supply hole 59, passes through the rear-side oil supply path 59b by being branched from the rear-side oil supply path 59a, and is supplied from the front-side oil supply path 49 to the front-side bearing 47 via the cylinder-side oil supply path 41.
The high-pressure oil O having been supplied to the front-side bearing 47 has intermediate pressure by being squeezed between the front-side bearing 47 and the drive shaft 27, and the oil O having been reduced to the intermediate pressure is supplied to the intermediate-pressure supply groove 51 through the gap between the drive shaft 27 and the front-side block 31a.
The high-pressure oil O having been 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 a rotation latter-half position of the rotor 23 to impart the back pressure for making the vane 25 project from the vane groove 75.
According to the gas compressor 1 of the present embodiment, the back pressure space 77 of the vane groove 75 having completed communication with the intermediate-pressure supply groove 67 communicates with the first supply section 69a of the high-pressure supply groove 69, and the high pressure is supplied from the first supply section 69a thereto.
Thereafter, this back pressure space 77 completes communication with the first supply section 69a before the back pressure space 77 of the next vane groove 75 that is positioned on the upstream side of the rotation direction X communicates with the first supply section 69a and communicates with the second supply section 69b that is independent of the first supply section 69a and is positioned on the downstream side of the rotation direction X, and thus the high pressure is again supplied to the back pressure space.
Accordingly, at a time point when the back pressure space 77 having completed communication with the intermediate-pressure supply groove 67 communicates with the first supply section 69a of the high-pressure supply groove 69, the preceding back pressure space 77 adjacent to the back pressure space 77 on the downstream side in the rotation direction X does not communicate with the first supply section 69a simultaneously.
In
Accordingly, the preceding back pressure space 77A adjacent to the back pressure space 77B on the downstream side in the rotation direction X does not communicate with the first supply section 69a simultaneously at a time point when the back pressure space 77B communicates with the first supply section 69a of the high-pressure supply groove 69. The similar relation is established not only between the back pressure space 77A and the back pressure space 77B, but also between the back pressure space 77B and the back pressure space 77C, and between the back pressure space 77C and the backpressure space 77A.
It is possible to prevent the pressure in the preceding back pressure space 77 from being temporarily lowered from the high pressure by the intermediate pressure before the following next back pressure space 77 rises to the high pressure, by allowing the two back pressure spaces 77 not to communicate with the first supply section 69a simultaneously. Accordingly, it is possible to prevent the occurrence of chattering in which the vane 25 repeats contact with and separation from the inner peripheral surface 33d of the cylinder chamber 33, by a temporary reduction of pressure in the back pressure space 77 of the vane 25 in the early stage of the compression process.
Furthermore, the back pressure space 77 completes communication with the second supply section 69b before the back pressure space 77 of the next vane groove 75 which is positioned on the upstream side in the rotation direction X communicates with the second supply section 69b. Accordingly, at a time point when the back pressure space 77 having completed communication with the first supply section 69a of the high-pressure supply groove 69 communicates with the second supply section 69b of the high-pressure supply groove 69, the preceding back pressure space 77 adjacent to the downstream side of the back pressure space 77 in the rotation direction X does not communicate with the second supply section 69b simultaneously.
As shown by P in the graph in
Furthermore, according to the gas compressor 1 of the present embodiment, the total of the communication cross-sectional areas Si and S3 of the back pressure space 77 with the first supply section 69a and the second supply section 69b when the communication destination of the back pressure space 77 shifts from the first supply section 69a to the second supply section 69b is set to be a minimum path cross-sectional area or more of the supply route of the high-pressure oil O to the first supply section 69a and the second supply section 69b.
In the middle stage of shifting the communication destination of the back pressure space 77 from the first supply section 69a to the second supply section 69b, the back pressure space 77 communicates, in the minimum path cross-sectional area or more, with at least one of the first supply section 69a or the second supply section 69b, and thus there can be ensured a destination to which the high pressure in the back pressure space 77 is released.
Accordingly, it is possible to prevent, as shown in the graph in
Thereby, there is prevented a phenomenon in which the pressing force of the vane 25 against the inner peripheral surface 33d of the cylinder chamber 33 is increased more than necessary by a temporary pressure increase in the back pressure space 77 and thus the sliding resistance between the both is increased. Therefore, it is possible to prevent increase in the sliding resistance of the vane 25 to the inner peripheral surface 33d of the cylinder chamber 33 due to increase in the power required for rotation of the rotor 23 by the temporary pressure increase in the back pressure space 77 in the later stage of the compression process and in the discharged process, thereby being able to maintain the operating performance as the gas compressor 1.
Note that it is desirable that the second supply section 69b of the high-pressure supply groove 69 be formed into a shape of the largest possible size in the rotation direction X within a range in which the two back pressure spaces 77 mutually adjacent in the rotation direction X of the rotor 23 do not simultaneously communicate with each other. Consequently, it is possible to allow the back pressure space 77 in which pressure has been increased from the intermediate pressure toward the high pressure due to communication with the first supply section 69a to communicate with the second supply section 69b from an earlier stage of the compression process of the compression chambers 33a, 33b and 33c, and thereafter to stabilize the pressure in the back pressure space 77 to the high pressure.
Accordingly, it is possible to start the discharged process of the compression chambers 33a, 33b and 33c at an earlier stage, the open/close valve 37 of the discharge slot 35 is opened at an earlier stage and the high-pressure refrigerant in the compression chambers 33a, 33b and 33c is efficiently and sufficiently discharged, and thereby it is possible to achieve enhancement of refrigerant compression efficiency.
In the present embodiment, it was assumed that the high-pressure supply groove 69 is divided into the two mutually independent first supply section 69a and second supply section 69b in the rotation direction X. However, the present invention is applicable also in a case where the high-pressure supply groove 69 is divided into three or more supply sections in the rotation direction X. In that case, the relation of the present invention is applied to the communication cross-sectional area of an upstream-side supply section or a downstream-side supply section with the back pressure space 77 when the back pressure space 77 moves striding over the two adjacent supply sections in the rotation direction X.
Next, the second embodiment of the present invention will be described with reference to
In the present embodiment, an interval 69c having a size that is not less than that of the back pressure space 77 of the vane groove 75 is provided between the first supply section 69a and the second supply section 69b in the rotation direction X of the rotor 23. Namely, the interval 69c provided between the first supply section 69a and the second supply section 69b is set larger than the width of the back pressure space 77 of the vane groove 75.
In a state shown in
In this state, the back pressure space 77A of the vane groove 75 in the vane 25A that precedes the vane 25B in the downstream side of the vane 25B in the rotation direction X of the rotor 23 has already completed communication with the second supply section 69b and starts to communicate with the intermediate-pressure supply section 67 that is positioned on the downstream side of the rotation direction X.
Here, there will be described the position of the interval 69c between the first supply section 69a and the second supply section 69b of the high-pressure supply groove 69 in the rotation direction X of the rotor 23. When the rotor 23 rotates in the rotation direction X after the state shown in
In this state, when the projection stroke of the vane 25B relative to the vane groove 75 is reduced along with rotation of the rotor 23 in the rotation direction X, the volume of the back pressure space 77B is reduced. At this time, since the back pressure space 77B is not in communication with any of the first supply section 69a and the second supply section 69b, it is not possible to release the high pressure of the amount corresponding to the reduced volume to them.
Accordingly, there is assumed a case where, when the vane 25B is in sliding contact with a region indicated by a range (A) in
In this case, the volume of the back pressure space 77B is reduced at a rate in accordance with a reduction rate of the projection stroke of the vane 25B in a state where the back pressure space 77B is isolated from the first supply section 69a and the second supply section 69b, and the pressure in the back pressure space 77B temporarily rises as indicated by P1 in
In a case where such a pressure rise of the back pressure space 77B is generated, the vane 25B which receives force acting in a direction of intruding into the vane groove 75 from the inner peripheral surface 33d of the cylinder chamber 33 attempts to project from the vane groove 75 by the risen pressure in the back pressure space 77B. Then, there is a possibility that the pressing force of the vane 25B against the inner peripheral surface 33d of the cylinder chamber 33 may be increased more than necessary and the sliding resistance between the vane 25B and the inner peripheral surface 33d of the cylinder chamber 33 may be increased.
Accordingly, it is configured such that a region in which the reduction rate of the projection stroke of the vane 25 relative to the vane groove 75 along with rotation of the rotor 23 in the rotation direction X on the inner peripheral surface 33d of the cylinder chamber 33 becomes a reduction rate not more than a predetermined threshold value which is lower than the above-mentioned constant rate is set as a region in which the reduction rate of the projection stroke is small, and the interval 69c is disposed so that the back pressure space 77 communicates with the interval 69c when the vane 25 comes into sliding contact with the region in which the reduction rate of the projection stroke concerned is small in the gas compressor 1 of the present embodiment.
Specifically, in the present embodiment, the inner peripheral surface 33d of the cylinder chamber 33 is, as shown in
(a) a region in which the projection stroke of the vane 25 that is in sliding contact with the inner peripheral surface 33d of the cylinder chamber 33 from the vane groove 75 is increased along with rotation of the rotor 23 in the rotation direction X;
(b) a region in which the projection stroke of the vane 25 that is in sliding contact with the inner peripheral surface 33d of the cylinder chamber 33 from the vane groove 75 is decreased along with rotation of the rotor 23 in the rotation direction X;
(c) a region in which the projection stroke of the vane 25 that is in sliding contact with the inner peripheral surface 33d of the cylinder chamber 33 from the vane groove 75 is decreased along with rotation of the rotor 23 in the rotation direction X and in which a reduction rate thereof is smaller than that in the region in (b); and
(d) a region in which the projection stroke of the vane 25 that is in sliding contact with the inner peripheral surface 33d of the cylinder chamber 33 from the vane groove 75 is decreased along with rotation of the rotor 23 in the rotation direction X and in which a reduction rate thereof is larger than that in the region in (c) and is smaller than that in the region in (b)
are sequentially successive in the rotation direction X of the rotor 23.
Accordingly, the interval 69c is disposed at a position where the back pressure space 77 communicates with the interval when the vane 25 is in sliding contact with the region (c) in which the reduction rate of the projection stroke of the vane 25 along with rotation of the rotor 23 in the rotation direction X is the smallest.
Next, an operation of the gas compressor 1 according to the present embodiment will be described.
Also in the present embodiment, at a time point when the back pressure space 77 having completed communication with the intermediate-pressure supply groove 67 communicates with the first supply section 69a of the high-pressure supply groove 69, the preceding back pressure space 77 adjacent to the back pressure space 77 on the downstream side in the rotation direction X does not communicate with the first supply section 69a simultaneously.
Accordingly, at a time point when the back pressure space 77 having completed communication with the intermediate-pressure supply groove 67 communicates with the first supply section 69a of the high-pressure supply groove 69, the preceding back pressure space 77 adjacent to the back pressure space 77 on the downstream side in the rotation direction X does not communicate with the first supply section 69a simultaneously.
It is possible to prevent the pressure in the preceding back pressure space 77 from being temporarily lowered from the high pressure by the intermediate pressure before the following next back pressure space 77 rises to the high pressure, by allowing the two back pressure spaces 77 not to communicate with the first supply section 69a simultaneously. Accordingly, it is possible to prevent the occurrence of chattering in which the vane 25 repeats contact with and separation from the inner peripheral surface 33d of the cylinder chamber 33, by a temporary reduction of pressure in the back pressure space 77 of the vane 25 in the early stage of the compression process.
Furthermore, the back pressure space 77 completes communication with the second supply section 69b before the back pressure space 77 of the next vane groove 75 which is positioned on the upstream side in the rotation direction X communicates with the second supply section 69b. Accordingly, at a time point when the back pressure space 77 having completed communication with the first supply section 69a of the high-pressure supply groove 69 communicates with the second supply section 69b of the high-pressure supply groove 69, the preceding back pressure space 77 adjacent to the downstream side of the back pressure space 77 in the rotation direction X does not communicate with the second supply section 69b simultaneously.
Accordingly, as shown in the graph in
Furthermore, according to the gas compressor 1 of the present embodiment, the interval 69c between the first supply section 69a and the second supply section 69b is positioned such that, when the back pressure space 77 communicates with the interval 69c between the first supply section 69a and the second supply section 69b, the vane 25 stored in the vane groove 75 of the back pressure space 77 comes into sliding contact with the region (c) in which the reduction rate of the projection stroke of the vane 25 along with rotation of the rotor 23 in the rotation direction X is the smallest.
Accordingly, when the back pressure space 77 communicates with the interval 69c between the first supply section 69a and the second supply section 69b, the projection stroke of the vane 25 is hardly reduced as shown by a part surrounded by a round frame in
Consequently, as indicated by P1 in the graph in
Thereby, there is prevented a phenomenon in which the pressing force of the vane 25 against the inner peripheral surface 33d of the cylinder chamber 33 is increased more than necessary by a temporary pressure increase in the back pressure space 77 and thus the sliding resistance between the both is increased. Therefore, it is possible to prevent increase in the sliding resistance of the vane 25 to the inner peripheral surface 33d of the cylinder chamber 33 due to increase in the power required for rotation of the rotor 23 by the temporary pressure increase in the back pressure space 77 in the later stage of the compression process and in the discharged process, thereby being able to maintain the operating performance as the gas compressor 1.
Note that it is desirable that the second supply section 69b of the high-pressure supply groove 69 be formed into a shape of the largest possible size in the rotation direction X within a range in which the two back pressure spaces 77 mutually adjacent in the rotation direction X of the rotor 23 do not simultaneously communicate with each other. Consequently, it is possible to allow the back pressure space 77 in which pressure has been increased from the intermediate pressure toward the high pressure due to communication with the first supply section 69a to communicate with the second supply section 69b from an earlier stage of the compression process of the compression chambers 33a, 33b and 33c, and thereafter to stabilize the pressure in the back pressure space 77 to the high pressure.
Accordingly, it is possible to start the discharged process of the compression chambers 33a, 33b and 33c at an earlier stage, the open/close valve 37 of the discharge slot 35 is opened at an earlier stage and the high-pressure refrigerant in the compression chambers 33a, 33b and 33c is efficiently and sufficiently discharged, and thereby it is possible to achieve enhancement of refrigerant compression efficiency.
Note that, although, in the present embodiment, the interval 69c provided between the first supply section 69a and the second supply section 69b is set larger than the width of the back pressure space 77 of the vane groove 75, the interval 69c may have a size smaller than that of the back pressure space 77 in the rotation direction X of the rotor 23. In this case, when the back pressure space 77 strides over the interval 69c in shifting the communication destination of the back pressure space 77 from the first supply section 69a to the second supply section 69b of the high-pressure supply section 69, the communication cross-sectional area of the back pressure space 77 for each of the supply sections 69a and 69b is reduced by an amount of overlapping the interval 69c.
Since the communication cross-sectional area is reduced, when the vane 25 intrudes into the back pressure space 77 side of the vane groove 75 along with rotation of the rotor 23 and the volume of the back pressure space 77 is reduced, efficiency of releasing the high pressure in the back pressure space 77 to the first supply section 69a and the second supply section 69b is reduced by the amount of the reduced volume. Then, there is a possibility that the pressure in the back pressure space 77 may temporarily rise in the later stage of the compression process and in the discharged process, the pressing force of the vane 25 against the inner peripheral surface 33d of the cylinder chamber 33 may be increased more than necessary and the sliding resistance between the vane 25 and the inner peripheral surface 33d of the cylinder chamber 33 may be increased.
However, the interval 69c is disposed at a position where the back pressure space 77 communicates with the interval 69c when the vane 25 is in sliding contact with the region (c) in which the reduction rate of the projection stroke of the vane 25 along with rotation of the rotor 23 in the rotation direction X is the smallest. Therefore, there can be prevented a temporary rise in the pressure in the back pressure space 77 by reduction in the releasing efficiency of the high pressure in the back pressure space 77. Accordingly, it is possible to prevent a phenomenon in which the sliding resistance of the vane 25 to the inner peripheral surface 33d of the cylinder chamber 33 is increased by the temporary pressure increase in the back pressure space 77 in the later stage of the compression process and in the discharged process and thus the power required for rotation of the rotor 23 is increased, thereby being able to maintain the operating performance as the gas compressor 1.
Note that, in the present embodiment, a region of the inner peripheral surface 33d of the cylinder chamber 33 with which the vane 25 comes into sliding contact when the back pressure space 77 communicates with the interval 69c was determined by the use of the reduction rate of the projection stroke of the vane 25 to the vane groove 75 as a standard. In the determination, an upper limit value of an allowable range of the reduction rate of the projection stroke of the vane 25 to the vane groove 75 is determined in accordance with an allowable range for a temporary increase in pressure in the back pressure space 77.
Then, the determined upper limit value is set as a predetermined threshold value, and there is determined a region in which the reduction rate of the projection stroke of the vane 25 on the inner peripheral surface 33d of the cylinder chamber 33 becomes not more than this threshold value. The interval 69c may be disposed such that, when the vane 25 comes into sliding contact with the thus determined region on the inner peripheral surface 33d of the cylinder chamber 33, the back pressure space 77 communicates with the interval 69c.
By making the determination in this way, it is possible to maintain the temporary pressure increase of the back pressure space 77 by a reduction in projection stroke of the vane 25 within the allowable range during a period when the back pressure space 77 is in communication with the interval 69c between the first supply section 69a and the second supply section 69b. Accordingly, it is possible to prevent increase in the sliding resistance of the vane 25 to the inner peripheral surface 33d of the cylinder chamber 33 due to increase in the power required for rotation of the rotor 23 by the temporary pressure increase in the back pressure space 77 in the later stage of the compression process and in the discharged process, thereby being able to maintain the operating performance as the gas compressor 1.
In the present embodiment, it has been made such that the high-pressure supply groove 69 is divided into the two mutually independent first supply section 69a and second supply section 69b in the rotation direction X. However, the present invention is applicable also in a case where the high-pressure supply groove 69 is divided into three or more supply sections in the rotation direction X. In that case, the relation of the present invention is applied to a relative position of the interval between the two supply sections adjacent to each other in the rotation direction X and the inner peripheral surface of the cylinder chamber.
In the above-mentioned plurality of embodiments, the second supply section 69b of the high-pressure supply groove 69 was set to have a size at which the two back pressure spaces 77 adjacent to each other in the rotation direction X of the rotor 23 do not communicate with each other simultaneously. For example, the second supply section 69b may have a space of a size larger than the size of the first supply section 69a in the rotation direction X. Consequently, it is possible to allow the back pressure space 77 in which pressure has been increased from the intermediate pressure toward the high pressure due to communication with the first supply section 69a to communicate with the second supply section 69b from an earlier stage of the compression process of the compression chambers 33a, 33b and 33c, and thereafter to stabilize the pressure in the back pressure space 77 to the high pressure.
Accordingly, it is possible to start the discharged process of the compression chambers 33a, 33b and 33c at an earlier stage, the open/close valve 37 of the discharge slot 35 is opened at an earlier stage and the high-pressure refrigerant in the compression chambers 33a, 33b and 33c is efficiently and sufficiently discharged, and thereby it is possible to achieve enhancement of refrigerant compression efficiency.
In addition, in the above-mentioned plurality of embodiments, a description has been made by taking, by way of example, a case of dividing the high-pressure supply groove 69 into two of the first supply section 69a and the second supply section 69b in the rotation direction X in order to prevent the back pressure space 77 of the vane 25 from communicating with the same supply section as that of the back pressure space 77 of the upstream-side vane 25 by way of example. However, the present invention is also widely applicable to a case where the high-pressure supply groove 69 is divided into three or more supply sections in the rotation direction X.
In that case, it is possible to obtain the similar effects to those of the above-mentioned plurality of embodiments by forming, among the three or more supply sections, one supply section that communicates with the back pressure space 77 that is in a state where the pressure in the back pressure space 77 is in the middle of rising from the intermediate pressure to the high pressure, into a shape in which the two back pressure spaces 77 adjacent to each other in the rotation direction X do not communicate with each other simultaneously.
Namely, the supply section positioned second from the most upstream side of the rotation direction X becomes at least an object to be formed into a shape in which the two back pressure spaces 77 adjacent to each other in the rotation direction X do not communicate with each other simultaneously. In addition, also each of the third and subsequent supply sections from the most upstream side becomes the object to be formed into a shape in which the two back pressure spaces 77 adjacent to each other in the rotation direction X do not communicate with each other simultaneously, in a case of communicating with the back pressure space 77 when the pressure of the back pressure space 77 is in the middle of rising from the intermediate pressure to the high pressure.
The above embodiments of the present invention are merely illustrative ones which have been described for facilitating understanding of the present invention and the present invention is not limited to the embodiments concerned. The technical scope of the present invention includes, not limited to specific technical matters disclosed in the above-mentioned embodiments, various modifications, changes, alternative technologies and the like, which can be easily derived therefrom.
The present application claims the priority based on Japanese Patent Application No. 2014-260491 filed on Dec. 24, 2014, based on Japanese Patent Application No. 2014-260492 filed on Dec. 24, 2014 and based on Japanese Patent Application No. 2014-260500 filed on Dec. 24, 2014, the entire contents of which are incorporated herein by reference.
According to the present invention, the back pressure space of the vane groove having completed communication with the intermediate-pressure supply section communicates with the first supply section of the high-pressure supply section until the refrigerant pressure in each of the compression chambers having been partitioned by the vane stored in the vane groove reaches the highest pressure, and then the high pressure is supplied from the first supply section. Thereafter, this back pressure space completes communication with the first supply section before the back pressure space of the next vane groove on the upstream side of the rotation direction communicates with the first supply section, and then communicates with the next second supply section that is independent of the first supply section and subsequently the high pressure is again supplied thereto.
Accordingly, at a time point when the back pressure space having completed communication with the intermediate-pressure supply section communicates with the first supply section of the high-pressure supply section, the preceding back pressure space which is adjacent to the back pressure space on the downstream side in the rotation direction does not communicate with the first supply section simultaneously. Consequently, the pressure in the preceding back pressure space is prevented from being temporarily lowered from the high pressure by the intermediate pressure of the following next back pressure space and the occurrence of chattering of the vane by a temporary reduction in pressure in the back pressure space of the vane can be prevented.
| Number | Date | Country | Kind |
|---|---|---|---|
| 2014-260491 | Dec 2014 | JP | national |
| 2014-260492 | Dec 2014 | JP | national |
| 2014-260500 | Dec 2014 | JP | national |
| Filing Document | Filing Date | Country | Kind |
|---|---|---|---|
| PCT/JP2015/085193 | 12/16/2015 | WO | 00 |
