JP6020029B2 - Vane type compressor - Google Patents

Description

  The present invention relates to a vane type compressor.

  A vane compressor used to compress a refrigerant generally has a housing in which a suction chamber, a discharge chamber, and a compression mechanism are formed. A drive shaft is rotatably supported by the housing. The compression mechanism includes a cylinder chamber, a rotor fixed to the drive shaft so as to be integrally rotatable, and a plurality of vanes provided in the rotor.

  Patent Document 1 describes a vane compressor in which a housing is formed of two members, a front housing and a rear housing. In the vane compressor disclosed in Patent Document 1, a plurality of bolts are used in addition to the seal member in order to ensure the surface pressure of the seal surface of the housing (the connection surface between the front housing and the rear housing member).

JP2012-26330A

  However, it is necessary to fasten the bolts while ensuring the surface pressure of the sealing surface. As a result, the structure of the fastening part becomes complicated, or the number of parts increases and the weight of the entire vane compressor increases. There was a problem. Further, it is necessary to appropriately manage the axial force when tightening the bolt, and the assembly of the vane compressor has become more complicated.

  The present invention has been made to solve such a problem, and an object thereof is to provide a vane type compressor having a small number of parts, a light weight, and a simple assembly process.

In order to solve the above problems, a vane compressor according to the present invention includes a drive shaft, a rotor attached to the drive shaft so as to be integrally rotatable, a vane attached to the rotor, a drive shaft, and a vane. A rotor assembly is disposed in the housing, and forms a compression chamber in cooperation with the vane and the rotor, and a shell including the bottom portion and the cylindrical portion for housing the housing assembly, The housing includes a shell having an annular groove formed on the peripheral surface, and a retaining ring that is disposed in the annular groove and maintains a housing state of the housing assembly with respect to the shell . The housing assembly has a recess that opens in a radial direction. The recess of the housing assembly forms a suction chamber with the inner peripheral surface of the cylindrical portion of the shell, and the suction chamber is provided between the compression chamber and the retaining ring in the axial direction in which the drive shaft extends.

The housing assembly of the vane compressor according to the present invention, the retaining ring may be restricted to movement in the axial direction against the shell.

  The shell has an opening at one end, the annular groove is formed in the opening, the housing assembly has an end surface in a direction intersecting the drive shaft, and the retaining ring is formed on the housing assembly. You may arrange | position in an annular groove so that it may contact | abut to an end surface.

Furthermore , it can have an annular elastic member that is disposed in contact with both the housing assembly and the shell in the axial direction and that can expand and contract in the axial direction.

Furthermore, the housing assembly may have a press-fit fitting portion with the shell.

  Further, the shell may have a rotation preventing portion that engages with the housing assembly and prevents the housing assembly from moving in the circumferential direction.

Also, shell has a stopper portion capable of constituting the discharge chamber to the space inside the shell by positioning the housing assembly, the housing assembly is inserted into the shell, by being positioned by the stopper portion , may be a discharge chamber between the shell and the housing assembly is formed.

  Further, the annular groove may be formed in a concave shape by the bottom surface and both side surfaces, and a relief portion may be formed at a corner portion formed by the bottom surface and one side surface.

  According to the present invention, in the vane type compressor, the number of parts can be reduced, the weight can be reduced, and the assembly process can be simplified.

It is sectional drawing of the vane type compressor which concerns on Embodiment 1 of this invention. It is sectional drawing which cut the vane type compressor of FIG. 1 along II-II, and is a figure which shows typically the mode in a cylinder chamber. It is sectional drawing which cut the vane type compressor of FIG. 1 along III-III, and is a figure which shows typically the arrangement | positioning and shape of a retaining ring. It is a figure showing the lower half of the cross section which cut the vane type compressor of Drawing 1 along IV-IV, and is a figure showing typically the composition of a detent mechanism. It is sectional drawing of the vane type compressor which concerns on Embodiment 2 of this invention. It is sectional drawing which cut the vane type compressor of FIG. 5 along VI-VI, and is a figure which shows the mode in a cylinder chamber typically. It is a figure which shows typically the shape of the retaining ring and annular groove of the vane type compressor which concerns on another embodiment of this invention. Fig.8 (a) is a figure which shows typically the shape of the annular groove of the vane type compressor which concerns on another embodiment of this invention. FIGS. 8B and 8C are views showing a reference example for explaining the annular groove of FIG. 8A.

Embodiment 1 FIG.
Hereinafter, the vane type compressor 101 which concerns on Embodiment 1 of this invention is demonstrated with reference to FIGS.
As shown in FIG. 1, the housing of the vane compressor 101 includes a housing assembly 2 composed of two members, a front housing 3 and a rear side plate 5 that are adjacent to and connected to each other. The front housing 3 and the rear side plate 5 are directly connected to each other by bolts 45. Further, the housing assembly 2 is press-fitted and accommodated inside the substantially cylindrical shell 7. The shell 7 includes a bottom portion 7f and a cylindrical portion 7g. The shell 7 has an opening 7h at one end opposite to the bottom 7f. Furthermore, three mounting legs 7 a are formed on the outer peripheral surface of the shell 7. The vane type compressor 101 is attached to the engine by the attachment foot 7a.

Referring to FIG. 1, an elliptical substantially cylindrical space having one end that is largely open is formed inside the front housing 3. The rear side plate 5 is in direct contact with the end surface of the front housing 3 and fastened by bolts 45. The rear side plate 5 has an opening in an elliptical substantially cylindrical space formed in the front housing 3. Close. The oval substantially cylindrical space closed in this way constitutes the cylinder chamber 13. Furthermore, a drive shaft 9 is rotatably supported by the front housing 3 and the rear side plate 5, and the drive shaft 9 is disposed so as to penetrate the center of the cylinder chamber 13. One end of the drive shaft 9 protrudes from the front housing 3 in the negative X-axis direction and is connected to an electromagnetic clutch, a pulley, and the like (not shown). Therefore, a driving force from a vehicle engine (not shown) is transmitted to the drive shaft 9.
Here, in the following description, the direction in which the drive shaft 9 extends is the X-axis direction, the direction from the front housing 3 toward the rear side plate 5 is the X-axis positive direction, and the direction from the rear side plate 5 to the front housing 3 is the X-axis negative. The direction.
The X axis direction constitutes the axial direction.

  As shown in FIG. 1, the front housing 3 has a donut-shaped recess 15 a that is adjacent to the cylinder chamber 13 and that can open in the radial direction about the drive shaft 9 and constitute the suction chamber 15. Therefore, the suction chamber 15 is formed by fitting the front housing 3 to the shell 7. An O-ring 19 is disposed between the front housing 3 and the shell 7 adjacent to the suction chamber 15 on the negative side in the X-axis direction. Further, a disc-shaped press-fitting fitting portion 3 b is formed on the outer periphery of the front housing 3 adjacent to the O-ring 19 on the X axis negative direction side. The front housing 3 is press-fitted to the shell 7 at a press-fitting fitting portion 3b. A suction port 7c is formed in the upper portion of the shell 7 at a position corresponding to the suction chamber 15, and the suction chamber 15 communicates with the outside through the suction port 7c.

  On the other hand, by fitting the rear side plate 5 to the shell 7, a discharge chamber 17 that is a substantially cylindrical space is formed between the rear side plate 5 and the shell 7. Here, an O-ring 12 is disposed between the outer peripheral surface of the rear side plate 5 and the inner peripheral surface of the shell 7. Further, a disk-shaped press-fitting portion 5b is formed adjacent to the O-ring 12 on the X axis positive direction side. The rear side plate 5 is press-fitted to the shell 7 at the press-fitting fitting portion 5b. Further, a discharge port 7 b is provided on the upper side of the shell 7 on the side opposite to the suction port 7 c with the cylinder chamber 13 interposed therebetween. The discharge chamber 17 communicates with the outside through the discharge port 7b. A separator 41 is formed on the rear side plate 5. The suction chamber 15 communicates with the cylinder chamber 13, and the discharge chamber 17 similarly communicates with the cylinder chamber 13 via the separator 41. That is, the refrigerant sent from the outside to the vane compressor 101 enters the suction chamber 15 via the suction port 7c, flows into the compression chamber 31 from the suction chamber 15, and is compressed. Then, after the lubricating oil and the like are removed by the separator 41, the compressed refrigerant flows out from the discharge port 7b through the discharge chamber 17.

  As shown in FIG. 2, the drive shaft 9 is disposed so that the center of the front housing 3 is the center of rotation. A cylindrical rotor 25 is attached to the drive shaft 9 so as to be integrally rotatable, and the rotor 25 is rotatably provided in a cylinder chamber 13 which is an elliptical, substantially cylindrical space. The rotor 25 is in contact with the inner peripheral surface of the cylinder chamber 13 at two contact points facing each other. Further, five vane grooves 25 a are formed on the outer peripheral surface of the rotor 25. The vane grooves 25a are arranged at equal intervals from each other around the rotation center O of the rotor 25. A vane 27 is accommodated in each vane groove 25a so as to be able to appear and retract. That is, the vane 27 is attached to the outer periphery of the rotor 25 through the vane groove 25a so as to be able to appear and retract. Further, a back pressure chamber 29 is formed between each vane 27 and each vane groove 25a. Here, the vane 27 is brought into contact with the inner peripheral surface of the cylinder chamber 13 when the lubricating oil is supplied as the back pressure from the back pressure chamber 29. The five compression chambers 31 are formed in the cylinder chamber 13 by the five vanes 27 and the outer peripheral surface of the rotor 25. That is, the drive shaft 9, the vane 27, and the rotor 25 are disposed inside the housing assembly 2, and the housing assembly 2 forms a compression chamber 31 in cooperation with the vane 27 and the rotor 25. The front housing 3 is formed with a suction port 15b on the inner peripheral surface of the cylinder chamber 13, and the suction port 15b communicates with the compression chamber 31 in the suction stroke. Further, a discharge space 33 is formed on the outer peripheral surface of the front housing 3 with the shell 7, and the discharge space 33 communicates with the compression chamber 31 in the discharge stroke via a discharge port 33a. Further, the discharge space 33 communicates with the separator 41 through the communication passage 33b.

Here, referring to FIGS. 1 and 3, the front housing 3 has one end face 3 a on the X axis negative direction side, and this end face 3 a extends in a direction intersecting the drive shaft 9. A circlip 16, which is a C-type concentric snap ring, is disposed at a position where it abuts against the end surface 3 a of the front housing 3. An annular groove 7e is formed in an annular shape on the inner peripheral surface of the cylindrical portion 7g in the opening 7h of the shell 7. The circlip 16 is disposed so as to engage with the annular groove 7e, and is fixed in the X-axis direction. The circlip 16 is an elastic body made of spring steel. Therefore, when the circlip 16 is arranged in the annular groove 7e, first, the circlip 16 is inserted into the shell 7 while applying a force to push the ring inward. Next, when the circlip 16 is aligned with the position corresponding to the annular groove 7e and the force for pushing and shrinking inward is removed, the circlip 16 is subjected to an elastic force to spread outward. For this reason, the circlip 16 is engaged with the annular groove 7e while being pressed against the annular groove 7e by an elastic force, and a portion protruding from the annular groove 7e to the inside of the shell 7 abuts the front housing 3.
The circlip 16 constitutes a retaining ring.

Further, a step 3 s is formed on the outer peripheral surface of the front housing 3, and a step 7 s is formed on the inner peripheral surface of the shell 7. Here, in the X-axis direction, a damper rubber 14, which is an annular elastic body, is sandwiched between the step portion 3 s of the front housing 3 and the step portion 7 s of the shell 7. It is arranged in contact with both. Since the damper rubber 14 can expand and contract in the X-axis direction, the housing assembly 2 can be properly positioned in the shell 7 even if the gap between the circlip 16 and the end surface 3a of the front housing 3 changes depending on the processing accuracy. it can.
The damper rubber 14 constitutes an elastic member.

Next, a structure for preventing movement of the housing assembly 2 in the shell 7 in the rotational direction will be described with reference to FIG.
As shown in FIGS. 1 and 4, in the rear side plate 5, a columnar detent 5 a is integrally formed at one end surface facing the discharge chamber 17 toward the lower side of the separator 41. Further, two projecting portions 7d project from the inner peripheral surface of the shell 7, and a rotation preventing groove 7d1 is formed between the two projecting portions 7d. The rotation stopper 5a and the protrusion 7d are configured so that the rotation stopper 5a can be inserted into the rotation prevention groove 7d1 when the rear side plate 5 is press-fitted into the shell 7 together with the front housing 3. That is, the detent groove 7d1 of the shell 7 engages with the housing assembly 2 to prevent the housing assembly 2 from moving in the circumferential direction.
Here, the protruding portion 7d and the rotation preventing groove 7d1 constitute a rotation preventing portion.

Next, the outline of the assembly order of the housing of the vane type compressor 101 will be described.
First, the front housing 3 in which the rotor 25 and the vanes are disposed and the rear side plate 5 are directly fastened by the bolts 45 to form the housing assembly 2. As a result, a compression chamber 31 is formed inside the housing assembly 2. Next, the housing assembly 2 is press-fitted into the shell 7, and the detent 5 a of the rear side plate 5 is engaged with the groove 7 d 1 of the protrusion 7 d of the shell 7. At this time, the projecting portion 7d of the shell 7 functions as a stopper portion, and the housing assembly 2 is not inserted into the inside of the shell 7, and a substantially cylindrical space is secured between the rear side plate 5 and the shell 7. While being positioned. This substantially cylindrical space constitutes the discharge chamber 17. Further, by inserting the housing assembly 2 into the shell 7, the recess 15 a of the front housing 3 forms the suction chamber 15 with the inner peripheral surface of the shell 7. Then, the circlip 16 is disposed in the annular groove 7e. Accordingly, the housing assembly 2 is restricted from moving in the X-axis direction with respect to the shell 7 by the circlip 16 in addition to the protrusion 7 d of the shell 7.

  As described above, by using the circlip 16, the housing assembly 2 is maintained in the accommodation state in the shell 7 without fastening the housing assembly 2 and the shell 7 using bolts, and the X with respect to the shell 7 is maintained. Axial movement is restricted. Therefore, the number of parts is reduced, and the weight reduction of the vane type compressor 101 is achieved. Further, since it is not necessary to manage the axial force of the bolt, the assembly process is simplified. Furthermore, when a failure or the like of the vane compressor 101 occurs, the vane compressor 101 can be easily disassembled and repaired simply by removing the circlip 16. Further, the space for the bolts and bolt holes in the housing assembly 2 and the shell 7 can be omitted, and a large suction chamber 15 and discharge chamber 17 can be secured.

In addition, since the damper rubber 14 is provided between the front housing 3 and the shell 7, vibration generated in the vane compressor 101 is suppressed. Further, the gap between the components is absorbed, and the circlip 16 is securely fixed in the X-axis direction with respect to the annular groove 7e. The damper rubber 14 also functions as a seal that prevents leakage of refrigerant from the cylinder chamber 13 to the suction chamber 15 or from the suction chamber 15 to the cylinder chamber 13.
Furthermore, in the present invention, the front housing 3 and the rear side plate 5 are press-fitted into the shell 7, and the detent 5 a of the rear side plate 5 is inserted between the protruding portions 7 d of the shell 7. Thereby, it is possible to prevent the front housing 3 and the rear side plate 5 from rotating inside the shell 7 without using a fastener such as a bolt.

Embodiment 2. FIG.
Next, a vane compressor 102 according to Embodiment 2 of the present invention will be described with reference to FIGS. In the second embodiment, the same reference numerals as those in FIGS. 1 to 4 are the same or similar components, and thus detailed description thereof is omitted.
As shown in FIGS. 5 and 6, the vane type compressor 102 has a cylinder chamber 13 ′ that is a substantially circular, substantially cylindrical space inside the housing assembly 2 ′. The rotation center O ′ of the rotor 25 ′ is eccentric with respect to the cylinder chamber 13 ′, and a part of the rotor 25 ′ is in contact with the inner peripheral surface of the cylinder chamber 13 ′. Further, two vane grooves 25a ′ are formed on the outer peripheral surface of the rotor 25 ′. The vane grooves 25a ′ are disposed at point-symmetric positions with respect to the rotation center O ′ of the rotor 25 ′. In each vane groove 25a ′, a vane 27 ′ is accommodated so as to appear and retract. Further, a back pressure chamber 29 'is formed between each vane 27' and each vane groove 25a '. Two compression chambers 31 ′ are formed in the cylinder chamber 13 ′ by the two vanes 27 ′ and the outer peripheral surface of the rotor 25 ′. The front housing 3 ′ is formed with a suction port 15b ′ on the inner peripheral surface of the cylinder chamber 13 ′, and the suction port 15b ′ communicates with the compression chamber 31 ′ in the suction stroke. Further, a discharge space 33 ′ is formed on the outer peripheral surface of the front housing 3 ′ with the shell 7, and the discharge space 33 ′ communicates with the compression chamber 31 ′ in the discharge stroke via the discharge port 33 a ′. To do. Further, the discharge space 33 ′ communicates with the separator 41 through the communication passage 33 b ′.

As described above, even if the cylinder chamber 13 ′ of the vane compressor 102 is a true circular, substantially cylindrical space, the housing assembly 2 ′ is disposed in the shell 7 by using the circlip 16. Positioned against. Therefore, like the vane type compressor 101 according to the first embodiment, the vane type compressor 102 can reduce the number of parts, achieve weight reduction, and simplify the assembly process.
Furthermore, since the cylinder chamber 13 ′ of the vane compressor 102 is a perfect circle with respect to the substantially elliptic cylinder chamber 13 of the vane compressor 101 according to the first embodiment, the manufacturing process is simplified. Further, since the number of the vanes 27 ′, the suction ports 15b ′, and the discharge ports 33a ′ of the vane compressor 102 is smaller than that of the vane compressor 101 of the first embodiment, the manufacturing process and the assembling process are simplified. At the same time, the number of parts can be reduced.

  In the first and second embodiments, the circlip 16 has a rectangular cross section with a certain thickness. However, the present invention is not limited to this, and an inclined surface 16c ′ is formed on the outside as shown in FIG. A formed circlip 16 'may be used. In this other embodiment, the shell 7 'to which the circlip 16' is fixed is formed with an annular groove 7e 'having an inclined surface 7e1' matching the shape of the circlip 16 'on the inner surface. With this configuration, the circlip 16 ′ is guided by the inclined surface 7 e 1 ′ and pressed against the front housing 3 in the X axis positive direction. Therefore, it is possible to secure a higher surface pressure on the seal surface between the front housing 3 and the shell 7.

  Further, as shown in FIG. 8A, the annular groove 37e formed on the inner periphery of the shell 37 may have an escape portion 37e2 on the radially outer side. Here, referring to FIG. 8A, the annular groove 37e is formed in a concave shape by a bottom surface 37e3 which is a cylindrical surface and two side surfaces 37e4 which are annular planes. The escape portion 37e2 is an annular groove having an arc cross section. In the bottom surface 37e3 of the annular groove 37e, a relief portion 37e2 is formed at a corner portion 38 formed by the bottom surface 37e3 and the side surface 37e4 on the X axis negative direction side. Since a large stress acts on the corner portion where the circlip 16 abuts in the annular groove 37e, if the corner portion 38 is a corner portion of 90 ° or the curvature radius is close to 0, the shell 37 may be damaged, but the escape By providing the portion 37e2, the stress can be dispersed. On the other hand, when the corner portion 48 of the annular groove 47e formed in the shell 47 has a large curvature radius as shown in FIG. 8B, the circlip 16 does not contact the bottom surface 47e3. Further, as shown in FIG. 8C, a relief portion 57e2 can be formed at the corner portion 58 on the side surface 57e4 of the annular groove 57e formed in the shell 57 on the X axis negative direction side. However, when the escape portion 57e2 is formed as shown in FIG. 8C, it is difficult to secure a contact surface between the circlip 16 and the side surface 57e4 of the annular groove 57e. Therefore, the shape of the relief portion provided in the annular groove is most effective when the relief portion 37e2 of the annular groove 37e shown in FIG.

Here, in the above embodiment, the housing assembly 2 is composed of two members. However, the housing assembly 2 may be composed of a plurality of housing constituent members, and a portion that forms the suction chamber 15 with respect to the front housing 3. The part forming the cylinder chamber 13 may be formed of a separate member. Further, the portion constituting the suction chamber 15 of the front housing 3 may be divided into a member disposed in the positive X-axis direction and a member disposed in the negative X-axis direction with the suction chamber 15 interposed therebetween.
Further, the number of mounting feet 7a formed on the outer peripheral surface of the shell 7 is not limited to three as shown in the above embodiment.
Further, in the above-described embodiment, the number of vanes 27 or 27 ′ is not limited to two or five, and a compression chamber may be formed in the cylinder chamber 13 or 13 ′ by two or more vanes.
In addition, the circlip 16 or 16 ′ is provided with not only the C-shaped concentric retaining ring of the above embodiment but also a C-shaped retaining ring provided with fitting holes at both ends so that a dedicated tool such as a pliers can be easily inserted. May be used.

  2, 2 'housing assembly, 3, 3' front housing (housing assembly), 3a end face, 5 rear side plate (housing assembly), 7, 7 ', 37 shell, 7d protrusion (rotation preventing portion, stopper portion) ), 7d1 Non-rotating groove (anti-rotation part), 7e, 7e ', 37e annular groove, 7f bottom part, 7g cylinder part, 7h opening part, 9 drive shaft, 14 damper rubber (annular elastic member), 15 suction chamber, 15a Concave part, 16, 16 'circlip (retaining ring), 17 discharge chamber, 25, 25' rotor, 27, 27 'vane, 31, 31' compression chamber, 37e2 relief part, 37e3 bottom face, 37e4 side face, 38 corner part, 101,102 Vane type compressor.

Claims (8)

A drive shaft;
A rotor attached to the drive shaft so as to be integrally rotatable;
A vane attached to the rotor;
A housing assembly in which the drive shaft, the vane, and the rotor are disposed, and form a compression chamber in cooperation with the vane and the rotor;
A shell comprising a bottom portion and a cylindrical portion and housing the housing assembly, wherein the annular groove is formed on the inner peripheral surface of the cylindrical portion;
A retaining ring that is disposed in the annular groove and maintains a housing state of the housing assembly with respect to the shell ;
The housing assembly has a recess that opens in a radial direction;
The recess of the housing assembly forms a suction chamber with the inner peripheral surface of the cylindrical portion of the shell,
In the axial direction in which the drive shaft extends, the suction chamber is a vane type compressor provided between the compression chamber and the retaining ring . Said housing assembly, vane compressor according to claim 1, which is restricting the movement of said axial with respect to the shell by the retaining ring. The shell has an opening at one end;
The annular groove is formed in the opening,
The housing assembly has an end surface in a direction intersecting the drive shaft,
The vane compressor according to claim 1 or 2, wherein the retaining ring is disposed in the annular groove so as to abut on the end face of the housing assembly. 4. The vane according to claim 1, further comprising an annular elastic member that is disposed in contact with both the housing assembly and the shell in the axial direction and that can expand and contract in the axial direction. Mold compressor. The vane compressor according to any one of claims 1 to 4, wherein the housing assembly includes a press-fitting fitting portion with the shell.   The vane type compressor according to any one of claims 1 to 5, wherein the shell includes a rotation preventing portion that engages with the housing assembly and prevents movement of the housing assembly in a circumferential direction. Before SL shell has a stopper portion capable of constituting the discharge chamber to position the housing assembly to the interior of the space of the shell,
The housing assembly is inserted into the shell, by being positioned by the stopper portion, any one of claims 1 to 6, the previous SL discharge chamber is formed between said shell said housing assembly The vane type compressor according to one item.   The annular groove is formed in a concave shape by a bottom surface and both side surfaces, and a relief portion is formed at a corner formed by the bottom surface and one of the side surfaces. Vane type compressor.

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