JP5430393B2 - Vane type compressor - Google Patents

Description

  The present invention relates to a vane compressor, and more particularly to a vane compressor that prevents oil from accumulating in a lower space between a cylinder in which a rotor is rotatably accommodated and a shell member surrounding the cylinder.

  As a vane type compressor provided with a shell member surrounding the periphery of a cylinder, for example, the one shown in Patent Document 1 described below is known. The vane type compressor is fixed to a drive shaft and rotatably accommodated in a cam ring (cylinder), a vane inserted into a plurality of vane grooves provided in the rotor, and one of the cam rings. A side member disposed on the end side, and a shell member surrounding the other end side and the outer peripheral surface of the cam ring, and the side member and the shell member pivotally support the drive shaft, and the side member and One of the shell members is provided with a high-pressure chamber in which an end surface facing the cam ring is recessed to communicate with the discharge port, and the vane is provided between the outer peripheral surface of the cam ring and the inner peripheral surface of the shell member. When a discharge valve storage chamber that can communicate with a compression chamber formed therebetween is provided, and the discharge valve storage chamber and the high pressure chamber are separated by a flange portion provided in the cam ring They communicate with each other through a through hole formed in the flange portion.

  As shown in FIG. 5, a discharge port 514 is provided on the outer peripheral surface of the cam ring 51 corresponding to the compression space 512. The discharge port 514 opens into a discharge valve accommodating chamber 515 formed between the outer peripheral surface of the cam ring 51 and the inner peripheral surface of the shell member 57, and the compression chamber 513 formed between the vanes is provided in the discharge port 514. It is possible to communicate with the discharge valve storage chamber 515 via the. The discharge port 514 is opened and closed by a discharge valve 516 housed in the discharge valve housing chamber 515.

International Publication WO 2008/026496 (International Application PCT / JP2007 / 0666338) Specification

  However, when the compressed working fluid is discharged to the discharge valve storage chamber 515 via the discharge port, the oil contained in the working fluid adheres to the inner surface of the discharge valve storage chamber 515, and as a result, the discharge valve storage chamber. Oil stays in the lower part of the shell member 57 of 515. Since the accumulated oil is no longer used for the lubrication of the compressor, it is necessary to predict in advance the amount of oil remaining in the lower portion of the shell member 57 and to enclose excess oil corresponding to the amount. Therefore, there is a disadvantage that the cost increases.

  In addition, in order to reduce the pulsation of the vane compressor, a device for reducing the pressure pulsation in the discharge path in the compressor is required. However, if this is realized by another member, the number of parts will be increased. Inviting and increasing the number of seals. Furthermore, in order to adjust the pressure pulsation, it is desirable to have a structure in which the discharge path can be easily adjusted.

  The present invention has been made in view of the above problems, and provides a vane compressor that prevents oil from accumulating in the lower part of the shell member of the vane compressor and reduces pulsation. Is the main purpose.

A vane type compressor according to the present invention is inserted into a fixing member in which a cylinder is formed, a rotor fixed to a drive shaft and rotatably accommodated in the cylinder, and a plurality of vane grooves provided in the rotor. And a shell member that at least surrounds the opening end side and the outer peripheral surface of the cylinder. The outer peripheral surface of the shell member is provided with a discharge port for discharging a working fluid, and the inner peripheral surface of the cylinder and the rotor A compression chamber defined by the vane is provided between the outer peripheral surface and the compression chamber via a discharge port that is opened and closed by a discharge valve between the outer peripheral surface of the cylinder and the inner peripheral surface of the shell member. and the vane-type compressor capable of communicating the discharge space is provided, wherein the discharge space is from the site where the discharge valve by a partition wall projecting from the vicinity of the discharge port as a boundary are provided Provided over the entire circumference about Linda, it is characterized in that leads to the discharge port of the hydraulic fluid discharged to the discharge space from the discharge port is passed through the lower side of the cylinder of the discharge space.

  As a result, the working fluid discharged from the compression chamber to the discharge space through the discharge port passes through the lower side of the cylinder and is guided to the discharge port. Sent downstream. For this reason, it becomes possible to prevent oil from accumulating in the lower part of the shell member.

  Further, in the above-described configuration, the discharge space changes the passage cross section of the working fluid in the circumferential direction by changing the passage area of the working fluid between the outer circumferential surface of the cylinder and the inner circumferential surface of the shell member in the circumferential direction. It should be increased or decreased several times.

  As a result, a discharge space in which the passage section is increased or decreased a plurality of times in the circumferential direction is formed around the cylinder, so that a large number of muffler chambers are formed in series, and the pulsation of the compressor is reduced by the multistage muffler effect. It becomes possible.

  Further, the fixing member is integrally formed with a side block that closes the rear side end surface of the cylinder, and the working fluid discharged into the discharge space has a through hole formed in a flange portion provided in the cylinder. It is preferable to guide the oil to the oil separator provided in the side block, and then guide to the discharge port.

  Thereby, the number of parts constituting the vane compressor can be reduced, and the oil sent to the downstream side from the discharge space together with the working fluid can be separated by the oil separator.

  Here, the discharge port is provided at one place in the circumferential direction in the vicinity of the through hole formed in the flange portion, and a partition wall that partitions the discharge space is provided between the discharge port and the through hole. The working fluid discharged from the discharge port may be guided to the through hole through the periphery of the cylinder.

  According to this configuration, since the working fluid discharged from the discharge port moves almost the entire circumference of the cylinder without flowing through the shortest distance, the oil that always passes through the lower part of the cylinder and tries to accumulate in the lower part of the shell member. It is possible to promote the attenuation of pulsation by securing the length of the passage to the through-hole while transporting to the downstream side.

  Further, the discharge port provided in the cylinder is provided at two locations in the circumferential direction, and a partition that partitions the discharge space between the one discharge port and the through hole formed in the flange portion, The working fluid discharged from each discharge port may flow around the cylinder in the same direction and be guided to the through hole.

  When the discharge ports are provided at two locations in the circumferential direction of the cylinder, the discharge ports are normally provided at cylinder positions that are symmetrical with respect to the drive shaft. It is possible to allow the working fluid discharged from one discharge port to pass through the lower side of the cylinder. For this reason, it becomes possible to convey the oil which is going to accumulate in the lower part of the shell member to the downstream side.

As described above, according to the present invention, the working fluid discharged from the discharge port to the discharge space passes through the lower side of the cylinder of the discharge space and is guided to the discharge port, whereby oil is collected in the lower part of the shell member of the compressor. Therefore, it is possible to prevent lubrication failure due to oil shortage and to reduce the oil replenishment amount.
In addition, by changing the passage area of the working fluid between the outer peripheral surface of the cylinder and the inner peripheral surface of the shell member in the circumferential direction, the passage section of the working fluid is increased or decreased a plurality of times in the circumferential direction by a multistage muffler effect. It becomes possible to attenuate the pulsation of the compressor.
Further, the fixing member is integrally formed with a side block that closes the rear end surface of the cylinder, and the working fluid discharged into the discharge space is side-connected through a through hole formed in a flange portion provided in the cylinder. By guiding to the oil separator provided in the block and then guiding it to the discharge port, the number of parts is reduced, and the oil that tries to accumulate in the lower part of the shell member is conveyed from the discharge space and is effective with the oil separator Can be separated.

FIG. 1 is a view showing a configuration example of a vane type compressor according to the present invention, (a) is a view showing a side cross section cut so that a discharge path and an oil separator appear, and (b) is a view It is a figure which shows the side cross section cut | disconnected so that the suction route and the oil storage chamber may appear. 2 is a view showing cross sections of various portions of the vane type compressor shown in FIG. 1. FIG. 2A is a cross-sectional view taken along line AA in FIG. 1, and FIG. Sectional drawing cut | disconnected by the B line is shown. FIG. 3 is a perspective view of a partially cutaway portion of the compressor according to the present invention, (a) is a view showing a state in which a shell member is partially cut away as viewed from the front side, and (b) is a rear view. It is a figure which shows the state which notched a part of shell member seen from the side, and a fixing member and a part of oil separator formed in this. FIG. 4 is a diagram illustrating a cross section of the vane type compressor according to the second embodiment, and is a diagram illustrating a cross section cut along the line BB in FIG. 1. FIG. 5 is a cross-sectional view of a conventional vane compressor.

  Hereinafter, the vane type compressor of the present invention will be described with reference to the drawings.

1 to 3 show a vane type compressor suitable for a refrigeration cycle using a refrigerant as a working fluid. The vane type compressor 1 includes a cylinder 8 a constituting a compression chamber 19, a rotor 4 rotatably accommodated in the cylinder 8 a and fixed to the drive shaft 3, and a plurality of vanes provided in the rotor 4. A vane 6 inserted into the groove 5, a rear side block 8b fixed to the rear side end surface of the cylinder 8a, and a shell member 9 surrounding the front side end surface and the outer peripheral surface of the cylinder 8a and fitted to the rear side block 8b. It is configured.

  The rear side block 8b is formed integrally with the rear side of the cylinder 8a that accommodates the rotor 4, and constitutes a fixing member 8 that forms a compression chamber 19 together with the cylinder 8a.

The shell member 9 is configured by integrating a front side block 9a that is in contact with the front side end surface of the cylinder 8a and a cylindrical portion 9b that is formed so as to surround the outer peripheral surfaces of the cylinder and the rear side block 8b.
Moreover, the housing of the vane type compressor 1 is configured by fixing the fixing member 8 and the shell member 9 with the fastening bolt 50.

  The drive shaft 3 is rotatably supported by a front side block 9a of the shell member 9 and a rear side block 8b of the fixing member 8 via a plain bearing. The shell member 9 has a suction port 14 and a discharge port 11 for the working fluid (refrigerant gas), and a suction space 14 that communicates with the suction port 12 and is configured with a recess 13 formed in the cylinder 8a. A discharge space 15 described later is defined by the cylinder 8a and the cylindrical portion 9b of the shell member 9, and this discharge space 15 is discharged through an oil separator 16 formed in the rear side block 8b of the fixed member 8. 11 communicates.

  The space surrounded by the cylinder 8a and the cross section of the rotor 4 are formed in a perfect circle, and the axial center of the cylinder 8a and the axial center of the rotor 4 are formed by the outer peripheral surface of the rotor 4 and the inner peripheral surface of the cylinder 8a. Are provided so as to be in contact with each other in one direction (offset by a half of the difference between the inner diameter of the cylinder 8a and the outer diameter of the rotor 4), and the inner peripheral surface of the cylinder 8a and the outer peripheral surface of the rotor 4 A compression space 18 is defined between the two. The compression space 18 is partitioned by the vanes 6 to form a plurality of compression chambers 19, and the volume of each compression chamber 19 is changed by the rotation of the rotor 4.

  In the shell member 9, a pulley 20 that transmits rotational power to the drive shaft 3 is rotatably mounted on a boss portion 9 c integrated with the front side block 9 a, and rotational power is driven from the pulley 20 via an electromagnetic clutch 21. It is transmitted to the shaft 3.

  Further, the cylinder 8a is formed with flange portions 8c and 8d projecting in the radial direction at both ends thereof. The front-side flange portion 8c is formed in a shape that matches the inner peripheral shape of the shell member 9, is fitted inside the shell member 9, is brought into contact with the end surface of the front side block 9a, and the rear-side flange portion 8c. The flange portion 8d is also formed in a shape that matches the inner peripheral shape of the shell member 9, and is fitted inside the shell member 9 to be hermetically sealed from the shell member by a sealing member such as an O-ring. .

  A suction port 22 that communicates with the suction space 14 and a discharge port 23 that communicates with the discharge space 15 are provided on the peripheral surface of the cylinder 8 a corresponding to the compression space 18. Therefore, when the cylinder 8a is fitted into the shell member 9, the suction space 14 communicates with the compression chamber 19 via the suction port 22, and between the outer peripheral surface of the cylinder 8a and the inner peripheral surface of the cylindrical portion 9b, A discharge space 15 whose end is defined by the flange portions 8 c and 8 d is formed, and the discharge space 15 can communicate with the compression chamber 19 via the discharge port 23. The discharge port 23 is opened and closed by a discharge valve 24 accommodated in the discharge space 15.

  The discharge space 15 is provided over a substantially entire circumference of the cylinder 8a from a portion where the discharge valve 24 is provided with a partition wall 25 protruding in the vicinity of the discharge port 23 of the cylinder 8a as a boundary. On the opposite side to the side where the discharge port 23 is provided, the oil separator 16 communicates with the oil separator 16 through a through hole 26 formed in the flange portion 8d, and communicates with the discharge port 11 via the oil separator 16. ing.

  Further, the discharge space 15 increases or decreases the passage section of the working fluid a plurality of times in the circumferential direction by changing the passage area of the working fluid between the outer circumferential surface of the cylinder 8a and the inner circumferential surface of the shell member 9 in the circumferential direction. Is configured.

  Specifically, as shown in FIGS. 2B, 3A, and 3B, a plurality (3 in this example) abuts the inner surface of the cylinder portion 9b with an interval on the outer peripheral surface of the cylinder 8a. The convex portions 8aa are provided with slits 8ab, and the working fluid moves through the discharge space 15 only through the slits 8ab. .

  The oil separator 16 is formed integrally with the rear side block 8b, and includes an oil separation chamber 28 formed in a cylindrical space communicating with a through hole 26 formed in the flange portion 8d. A substantially cylindrical separation tube (separator pipe) 29 formed integrally with the rear side block 8b is disposed in the chamber 28 coaxially.

  The oil separation chamber 28 is formed so as to extend in a direction substantially orthogonal to the axial direction of the drive shaft 3 and to have its axis inclined obliquely with respect to the vertical line. It communicates with the discharge port 11 of the shell member 9 through the cylinder 29, and the lower end is opened on the side surface of the rear side block 8b. The opening at the lower end of the oil separation chamber 28 is airtightly closed by the cylindrical portion 9 b of the shell member 9. In this example, the cylinder portion 9b is extended in the axial direction so that the entire rear side block 8b is accommodated, and the oil separation chamber 28 is arranged in the circumferential direction of the rear side block 8b before and after the axial direction of the compressor. A space between the cylindrical portion 9b of the shell member 9 is hermetically sealed by a provided sealing member such as an O-ring.

  Accordingly, the working fluid that has flowed into the oil separation chamber 28 swirls around the separation cylinder 29 accommodated in the oil separation chamber 28, and the mixed oil is separated in the process, and the discharge gas from which the oil has been separated is separated. Is delivered to the discharge port 11 via the separation cylinder 29. The separated oil is formed at the bottom of the fixing member 8 through an oil discharge hole 30 formed between the fixing member 8 and the shell member 9 so as to communicate with the lower end of the oil separation chamber 28. The oil is stored in the oil storage chamber 31 and then supplied to the lubrication portion of the compressor via the oil supply passage 40.

  In the above configuration, rotational power from a power source (not shown) is transmitted to the drive shaft 3 via the pulley 20 and the electromagnetic clutch 21, and when the rotor 4 rotates, the working fluid flowing into the suction space 14 from the suction port 12 is transferred. The air is sucked into the compression space 18 through the suction port 22. Since the volume of the compression chamber 19 partitioned by the vanes 6 in the compression space 18 changes with the rotation of the rotor 4, the working fluid confined between the vanes 6 is compressed and is discharged from the discharge port 23 via the discharge valve 24. And discharged into the discharge space 15. The working fluid protruding into the discharge space 15 moves in the circumferential direction along the outer peripheral surface of the cylinder 8a (along the inner peripheral surface of the cylindrical portion 9b of the shell member 9) and passes below the cylinder 8a. The cylinder 8a is substantially circled around the circumference of the cylinder 8a and is introduced into the oil separation chamber 28 of the oil separator 16 formed integrally with the rear side block 8b through a through hole 26 formed in the flange portion 8d. It is discharged from the outlet 11 to the external circuit.

  Therefore, in the process in which the working fluid discharged from the discharge port 23 moves in the discharge space 15 formed between the cylinder 8a and the shell member 9 from the portion where the discharge port 23 faces to the portion where the through hole 26 faces. Since the oil passes through the lower part of the cylinder 8a, it is possible to prevent oil from accumulating in the lower part of the shell member 9, and to reduce the amount of oil replenishment.

  Further, in the discharge space 15 formed between the cylinder 8a and the cylinder portion 9b, there is a muffler chamber in which the areas of the outer peripheral wall of the cylinder 8a and the inner peripheral wall of the cylinder portion 9b are increased before and after each convex portion 8aa. Since these muffler chambers communicate with each other through the slits 8ab formed in the convex portion 8aa and are connected in series, the working fluid moves in the circumferential direction along the outer peripheral surface of the cylinder 8a. The chamber and the slit 8ab are alternately passed a plurality of times and moved to the through hole 26. For this reason, a multistage muffler effect can be obtained and pulsation can be reduced. Further, since the oil is guided to the oil separation chamber 28 of the oil separator 16 only through the through hole 26 of the flange portion 8d, the pressure pulsation of the discharge gas is reduced in the process of passing through the through hole 26, and further, the oil separator In the process of passing through 16, the pressure pulsation is reduced, and the pressure pulsation is sent out from the discharge port 11 in an extremely small state.

  Further, in the above-described compressor, the rear side block 8b is formed integrally with the rear side of the cylinder 8a that accommodates the rotor 4, and constitutes the fixing member 8 that forms the compression chamber 19 together with the cylinder 8a. Since the fixing member 8 is accommodated in the shell member 9 in which the front side block 9a and the cylindrical portion 9b are integrally formed, the number of parts of the compressor can be reduced. In addition, the oil separator 16 is formed integrally with the rear side block 8b of the fixing member 8, and is extended so as to cover the cylindrical portion 9b of the shell member 9 to the rear side end portion of the rear side block 8b. Since the tube portion 9b is airtightly closed, a closing member for closing the oil separation chamber 28 is not required, and the increase in the number of parts due to the oil separator 16 is eliminated.

Moreover, in Example 1, although the example applied to the vane type compressor which provided the discharge port 23 of the cylinder 8a in one place in the circumferential direction was shown, the conventional vane which provided the discharge port 23 in two places in the circumferential direction was shown. It may be applied to a mold compressor. Specifically, as shown in FIG. 4, the cylinder 8a is provided with discharge ports 23a and 23b at positions symmetrical to the drive shaft 3, and the cylinder 8a communicates with one of the discharge ports 23a. A partition wall 25 that partitions the discharge space 15 is provided between the hole 26, and two convex portions 8aa that are in contact with the inner surface of the cylindrical portion 9b are provided between one discharge port 23a and the other discharge port 23b. Is provided between the discharge port 23b and the through-hole 26, and a projection 8aa that abuts the inner surface of the cylindrical portion 9b is provided, and a slit 8ab that allows the working fluid to pass therethrough is formed in the three projections 8aa. .
In addition, since the other structure is the same as that of the said Example, the same code | symbol is attached | subjected to the same location and description is abbreviate | omitted.

  In the vane type compressor 1 having such a configuration, since the partition wall 25 is provided between the one discharge port 23a and the through hole 26, the working fluid compressed in the compression chamber 19 is discharged from the discharge ports 23a and 23b. And flows in the same direction toward the through hole 26 around the cylinder 8a (in the figure, counterclockwise). For this reason, the working fluid discharged from one discharge port 23a can pass through the lower side of the cylinder, and it is possible to convey oil to be stored in the lower part of the shell member 9 to the downstream side. It is possible to achieve the same function and effect.

  In the above configuration, the example of the vane type compressor in which the rear side block 8b is integrally formed with the cylinder 8a is shown. However, the present invention is applied to a vane type compressor in which the cylinder 8a and the rear side block 8b are separated. May be. Further, in the above-described configuration, the oil separator 16 is provided in the rear side block 8b integrated with the cylinder 8a, and this is accommodated in the shell member 9. However, the oil is added to the front side block integrated with the cylinder. In the configuration in which the separator is provided and accommodated in the shell member, the same configuration as described above may be employed.

Moreover, in the above-described configuration, the structure of the vane type compressor that is formed so as to change the passage cross section of the working fluid in the discharge space 15 in the circumferential direction by providing the slit 8ab in the convex portion 8aa is shown. You may make it change the channel | path cross section of the discharge path 15 to the circumferential direction using the shape of the bolt fastening part 60 which fastens the member 8 and the shell member 9. FIG. Specifically, as shown in FIG. 1, a plurality of bolt fastening portions 60 are formed to protrude in the circumferential direction on the outer peripheral surface of the cylinder 8a, and the axial length thereof is shorter than the axial length of the cylinder 8a. By doing so, the cross section of the passage is changed in the circumferential direction.
By adopting such a configuration, the multistage muffler effect can be obtained similarly to the vane type compressor having the above configuration, and pulsation can be reduced.

  Further, in the above-described configuration, the working fluid discharged from the discharge port 23 to the discharge space 15 is allowed to pass through the lower side of the cylinder 8a, and then is passed through the through hole 26 formed in the flange portion 8d. However, the present invention is not limited to this, and the discharge port 11 is provided on the outer peripheral surface of the shell member 9 so as to face the discharge space 15, and the working fluid passes through the lower side of the cylinder 8 a of the discharge space 15. After making it discharge, you may comprise so that it may discharge directly from the discharge outlet 11. FIG.

1 Vane type compressor 3 Drive shaft
4 Rotor 5 Vane Groove 6 Vane 8 Side Block 8a Cylinder 8c, 8d Flange 9 Shell Member 11 Discharge Port 15 Discharge Space 16 Oil Separator 19 Compression Chamber 23 Discharge Port 26 Through-hole

Claims (5)

A fixing member formed with a cylinder;
A rotor fixed to the drive shaft and rotatably accommodated in the cylinder;
A vane inserted into a plurality of vane grooves provided in the rotor;
A shell member that at least surrounds the opening end side and the outer peripheral surface of the cylinder,
A discharge port for discharging the working fluid is provided on the outer peripheral surface of the shell member,
A compression chamber defined by the vane is provided between the inner peripheral surface of the cylinder and the outer peripheral surface of the rotor;
In the vane type compressor in which a discharge space is provided between the outer peripheral surface of the cylinder and the inner peripheral surface of the shell member via a discharge port that is opened and closed by a discharge valve .
The discharge space is provided over substantially the entire circumference of the cylinder from a portion where the discharge valve is provided with a partition wall protruding in the vicinity of the discharge port as a boundary,
The vane type compressor characterized in that the working fluid discharged from the discharge port to the discharge space is guided to the discharge port through the lower side of the cylinder of the discharge space.   The discharge space increases or decreases the passage cross section of the working fluid a plurality of times in the circumferential direction by changing the passage area of the working fluid between the outer peripheral surface of the cylinder and the inner peripheral surface of the shell member in the circumferential direction. The vane type compressor according to claim 1.   The fixing member is integrally formed with a side block for closing the rear end face of the cylinder, and the working fluid discharged into the discharge space is passed through a through hole formed in a flange portion provided in the cylinder. The vane type compressor according to claim 1, wherein the vane type compressor is guided to an oil separator provided in the side block and then guided to the discharge port. The discharge port, wherein in the vicinity of the flange portion formed through holes provided in one location in the circumferential direction, the discharge port is provided the partition wall for partitioning the discharge space between the hole and the discharge port 4. The vane compressor according to claim 3 , wherein the working fluid discharged from the cylinder passes through the cylinder and is guided to the through hole. Discharge port provided in said cylinder is provided with the partition wall for partitioning the discharge space between the circumferential direction of one of said discharge port and said flange portion formed hole with provided at two positions, respectively 4. A vane type compressor according to claim 3 , wherein the working fluid discharged from the discharge port is caused to flow around the cylinder in the same direction and guided to the through hole.

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