JP7263071B2 - open compressor - Google Patents

Description

The present invention relates to an open compressor.

2. Description of the Related Art Conventionally, an open type compressor is known in which one end of a drive shaft, which is rotatably supported inside a housing via a bearing, protrudes outside the housing and is driven by external power (for example, , see Patent Document 1). The open type compressor of Patent Document 1 rotatably supports a crankshaft that drives an orbiting scroll by a main bearing and a sub-bearing. The main bearing is held by the front housing while being press-fitted into the end of the front housing on the side of the scroll compression mechanism.

JP 2016-156310 A

In the open-type compressor disclosed in Patent Document 1, the main bearing is press-fitted into the front housing through an opening on the side of the scroll compression mechanism of the front housing and held by the front housing. In order to press-fit the main bearing into the front housing, the opening of the front housing on the side of the scroll compression mechanism is made larger than the outer diameter of the main bearing. When the size of the main bearing is increased, the diameter of the opening of the front housing must be increased accordingly, resulting in an increase in the overall size of the compressor.

SUMMARY OF THE INVENTION The present invention has been made in view of such circumstances, and provides an open type compressor capable of holding an enlarged bearing portion inside without enlarging the housing that holds the bearing portion. intended to provide

In order to solve the above problems, an open compressor according to one aspect of the present invention employs the following means.
An open type compressor according to an aspect of the present invention includes a compression mechanism that is driven by a drive shaft that rotates about an axis and that compresses a fluid that flows in from a suction port and discharges the fluid from a discharge port, and supports the drive shaft. a bearing, a tubular first housing that accommodates the compression mechanism, and a recess that is attached to close an opening of the first housing and holds the bearing on the axis. a second housing formed at the end on the compression mechanism side, and a retaining member attached to the end of the second housing on the compression mechanism side with the bearing portion held in the recess. and, the recess has a cylindrical first inner peripheral surface having a first diameter centered on the axis, and the removal prevention member is larger than the first diameter centered on the axis A cylindrical second inner peripheral surface having a smaller second diameter is provided, and the bearing portion has a cylindrical outer peripheral surface having a third diameter larger than the second diameter.

According to the open type compressor according to one aspect of the present invention, the diameter of the second inner peripheral surface of the retaining member is larger than the first diameter of the first inner peripheral surface of the recess of the second housing in which the bearing portion is held. The second diameter is small. By making the second diameter smaller than the first diameter, the diameters of the outer peripheral surface of the retaining member and the outer peripheral surface of the second housing can accordingly be made smaller. Therefore, when the bearing portion is enlarged, it is possible to prevent the second housing from being enlarged accordingly.

Further, the third diameter of the outer peripheral surface of the bearing portion is larger than the second diameter of the second inner peripheral surface of the retaining member. By making the third diameter larger than the second diameter, the detachment prevention member prevents the bearing from detaching from the second housing. Thus, according to the open type compressor according to the aspect of the present invention, it is possible to hold the enlarged bearing portion inside without increasing the size of the housing that holds the bearing portion.

In an open type compressor according to an aspect of the present invention, the compression mechanism has a fixed scroll fixed to the first housing and an orbiting scroll connected to a crank pin eccentric with respect to the drive shaft. and a mechanism for compressing a fluid by orbiting the orbiting scroll meshed with the fixed scroll, and comprising an anti-rotation mechanism for preventing the orbiting scroll from rotating with respect to the crankpin. It's okay.

According to the open type compressor of this configuration, by orbiting the orbiting scroll connected to the drive shaft with respect to the fixed scroll fixed to the first housing, it is formed between the fixed scroll and the orbiting scroll. A fluid is compressed in the compression chamber. Since the anti-rotation mechanism prevents the orbiting scroll from rotating with respect to the crank pin, the fluid can be appropriately compressed by the compression chamber.

In the open type compressor configured as described above, the anti-rotation mechanism is formed in a plurality of anti-rotation pins attached to the end of the orbiting scroll on the second housing side and protruding along the axis, and in the removal prevention member. and a plurality of anti-rotation holes each having a cylindrical inner peripheral surface for accommodating the tips of the anti-rotation pins.
By inserting a plurality of anti-rotation pins attached to the orbiting scroll into a plurality of rotation-preventing holes formed in the disengagement prevention member, the orbiting scroll is prevented from rotating with respect to the crank pin, and the fluid is properly supplied to the compression chamber. can be compressed.

In the open type compressor configured as described above, the anti-rotation mechanism includes a plurality of anti-rotation pins that are attached to the end of the orbiting scroll side of the disengagement prevention member and protrude along the axis, and are formed on the orbiting scroll. and a plurality of anti-rotation holes each having a cylindrical inner peripheral surface for accommodating the distal ends of the anti-rotation pins.
By inserting a plurality of anti-rotation pins attached to the disengagement prevention member into a plurality of rotation-prevention holes formed in the orbiting scroll, the orbiting scroll is prevented from rotating with respect to the crank pin, and the fluid is properly supplied to the compression chamber. can be compressed.

In the open compressor configured as described above, the orbiting scroll is made of aluminum or an aluminum alloy, the anti-rotation pin is made of cast iron or steel, and the anti-rotation mechanism is made of the anti-rotation hole. and an annular member made of iron or a steel material containing iron.

When the orbiting scroll is made of an aluminum alloy and the anti-rotation pin is made of cast iron or steel, the hardness of the aluminum alloy is low. Therefore, direct contact between them causes wear of the orbiting scroll. In the open type compressor configured as described above, the annular member made of cast iron or steel material is held on the inner peripheral surface of the rotation prevention hole, so that wear of the orbiting scroll can be suppressed.

In the open type compressor according to one aspect of the present invention, a rod-shaped member extending along the axis and having a circular cross section can be inserted into the first mounting surface of the second housing to which the removal prevention member is mounted. A first positioning hole may be formed, and a second positioning hole into which the rod-shaped member can be inserted may be formed in a second mounting surface of the removal prevention member mounted on the second housing.

One end of the rod-shaped member is inserted into the first positioning hole formed in the first mounting surface of the second housing, and the other end of the rod-shaped member is inserted into the second positioning hole formed in the second mounting surface of the retaining member. Thereby, the retaining member is positioned with respect to the second housing. Therefore, the retaining member can be fixed to the second housing while the retaining member is positioned with respect to the second housing.

In an open type compressor according to an aspect of the present invention, the retaining member includes a retaining surface orthogonal to the axis and in contact with or close to a contact surface of the bearing on the compression mechanism side, and a retaining surface perpendicular to the axis. and a sliding surface in contact with or in close proximity to the end surface of the orbiting scroll on the side of the second housing.
The retaining surface of the retaining member is brought into contact with the contact surface of the bearing on the side of the compression mechanism, thereby preventing the bearing from detaching from the second housing. In addition, the disengagement prevention member can move the orbiting scroll in the direction along the axis of the drive shaft (thrust direction) without providing a separate thrust plate by bringing the sliding surface into contact with the end surface of the orbiting scroll on the second housing side. can support

In the open compressor configured as described above, the removal prevention member is formed with an insertion hole that opens toward the compression mechanism and into which a fastening bolt is inserted, and the sliding surface is the head of the fastening bolt. may be arranged on the side of the compression mechanism along the axis.
According to such an open type compressor, the sliding surface is arranged closer to the compressor than the head of the fastening bolt, so the fastening bolt is used to fasten the removal prevention member to the second housing, and the removal prevention member is secured to the second housing. The sliding surface of the member can be used to support the orbiting scroll in the direction along the axis of the drive shaft (thrust direction).

In an open type compressor according to an aspect of the present invention, the retaining member may be made of cast iron or steel, and the orbiting scroll may be made of aluminum or an aluminum alloy.
Since the disengagement prevention member is made of cast iron or steel, it is possible to suppress wear of the disengagement prevention member when the disengagement prevention member and the orbiting scroll are in direct contact with each other, compared to aluminum or aluminum alloy. .

ADVANTAGE OF THE INVENTION According to this invention, the open type compressor which can hold|maintain an enlarged bearing part inside can be provided, without enlarging the housing which hold|maintains a bearing part.

1 is a longitudinal sectional view showing an open compressor according to a first embodiment of the present invention; FIG. 2 is a view of the front housing and the retaining member of the open type compressor shown in FIG. 1 as viewed along the axis of the drive shaft; FIG. 2 is a longitudinal sectional view showing a state in which a main bearing is press-fitted into the front housing of the open compressor shown in FIG. 1; FIG. FIG. 5 is a vertical cross-sectional view showing an open compressor according to a second embodiment of the present invention; 5 is a view of the front housing and the retaining member of the open compressor shown in FIG. 4 as viewed along the axis of the drive shaft; FIG. FIG. 6 is a longitudinal sectional view showing an open compressor according to a third embodiment of the present invention; FIG. 7 is a view of the front housing and the retaining member of the open compressor shown in FIG. 6 as viewed along the axis of the drive shaft;

[First embodiment]
An open compressor 1 according to a first embodiment of the present invention will be described below with reference to the drawings. FIG. 1 is a longitudinal sectional view showing an open compressor 1 of this embodiment. 2 is a view of the front housing 3 and the retaining member 31 of the open compressor 1 shown in FIG. 1 as viewed along the axis X of the drive shaft 6. FIG. FIG. 2 is a view of the open compressor 1 viewed from the direction of arrow H in FIG. 1, showing a state in which the scroll compression mechanism 5 and the rear housing 2 are removed. The vertical cross-sectional view shown in FIG. 1 is a cross-sectional view taken along the line A--X--A in FIG. FIG. 3 is a longitudinal sectional view showing a state in which the main bearing 7 is press-fitted into the front housing 3 of the open compressor 1 shown in FIG. FIG. 3 shows a state in which the scroll compression mechanism 5, the rear housing 2, and the retaining member 31 are removed.

As shown in FIG. 1, an open scroll compressor (open compressor) 1 of this embodiment includes a cylindrical rear housing 2 (first housing) extending in a circumferential direction around an axis X, a rear A front housing 3 (second housing) attached so as to close an opening 2a provided on the front end side of the housing 2 is provided.

Further, the open compressor 1 of this embodiment includes a scroll compression mechanism 5, a drive shaft 6, a main bearing (bearing portion) 7, a sub-bearing 8, a lip seal 9, a bearing 10, and a pulley 11. , an electromagnetic clutch 12 , a crank pin 13 , a variable orbiting radius mechanism 14 , a fixed scroll 15 , an orbiting scroll 16 , a balance weight 30 , a slip-off preventing member 31 , and an Oldham link 32 .

The rear housing 2 has a closed rear end, and the front housing 3 is fixed to the front opening 2a by bolts (not shown). A sealed space is formed inside the front housing 3 fixed to the rear housing 2, and the scroll compression mechanism 5 and the drive shaft 6 are accommodated in the sealed space. On the outer peripheral surface of the rear housing 2, there are an intake port IN through which fluid (refrigerant gas) flows into the sealed space, and a discharge port (not shown) through which the fluid compressed by the scroll compression mechanism 5 is discharged from the sealed space to the outside. formed.

The front housing 3 has a recess 3a for holding the main bearing 7 on the axis X and a recess 3b for holding the sub-bearing 8 on the axis X. The rear housing 2 side is open. It is a substantially cylindrical member. The recess 3b is formed at the end on the scroll compression mechanism 5 side.

The drive shaft 6 is rotatably supported by the front housing 3 via a main bearing 7 and a sub-bearing 8 . At the front end of the drive shaft 6 projecting outside from the front housing 3 through a lip seal 9, a pulley 11 rotatably mounted on the outer periphery of the front housing 3 via a bearing 10 engages an electromagnetic clutch 12. connected through In this manner, the drive shaft 6 receives external power for driving the pulley 11 through the electromagnetic clutch 12, and rotates around the axis X shown in FIG.

A crankpin 13 is integrally provided at the rear end of the drive shaft 6 and is eccentric by a predetermined dimension. The rear end of the drive shaft 6 is connected to an orbiting scroll 16 of the scroll compression mechanism 5, which will be described later, via a known variable orbiting radius mechanism 14 including a drive bush for varying the orbiting radius. A balance weight 30 is attached to the variable orbiting radius mechanism 14 to balance the weight with the orbiting scroll 16 attached eccentrically to the drive shaft 6 .

The scroll compression mechanism 5 is driven by a drive shaft 6 that rotates about the axis X and is formed in the rear housing 2 by compressing a fluid (refrigerant gas) flowing in from an inlet IN formed on the outer peripheral surface of the rear housing 2 . It is a mechanism for ejecting from an ejection port (not shown). The scroll compression mechanism 5 includes a fixed scroll 15 and an orbiting scroll 16 made of, for example, an aluminum alloy.

The scroll compression mechanism 5 engages a pair of fixed scrolls 15 and orbiting scrolls 16 with a phase difference of 180 degrees to cause the orbiting scrolls 16 to revolve around the axis X. As shown in FIG. The scroll compression mechanism 5 forms a pair of compression chambers between the fixed scroll 15 and the orbiting scroll 16, and compresses the fluid (refrigerant gas) by moving the fluid while gradually decreasing the volume from the outer peripheral position to the central position. do.

The fixed scroll 15 is provided with a discharge port (not shown) for discharging compressed fluid at its central portion, and is fixed to the bottom wall surface of the rear housing 2 via bolts (not shown). The orbiting scroll 16 is connected to the crank pin 13 of the drive shaft 6 via the variable orbiting radius mechanism 14, and revolves via the Oldham link 32 on the surface of the anti-slip member 31 of the front housing 3 on the side of the scroll compression mechanism 5. It is supported so as to be rotatable. The crank pin 13 is arranged eccentrically with respect to the axis X of the drive shaft 6 .

The fixed scroll 15 and the orbiting scroll 16 each have a structure in which a spiral wrap is erected on an end plate arranged on a plane perpendicular to the axis X. As shown in FIG. Between the fixed scroll 15 and the orbiting scroll 16, a pair of compression chambers partitioned by respective end plates and respective spiral wraps are formed symmetrically with respect to the scroll center. Further, the orbiting scroll 16 is driven to smoothly revolve around the fixed scroll 15 .

The main bearing 7 supports the drive shaft 6 on the axis X. The inner ring 7a is press-fitted onto the drive shaft 6, and the outer ring 7b is press-fitted to the end of the front housing 3 on the scroll compression mechanism 5 side. . The main bearing 7 is held on the axis X by the front housing 3 . The main bearing 7 is a radial ball bearing arranged closer to the scroll compression mechanism 5 than the sub-bearing 8 and having an outer diameter larger than that of the sub-bearing 8 . The end surface of the outer ring 7b of the main bearing 7 on the side of the scroll compression mechanism 5 forms a contact surface that comes into contact with or comes close to the coming-off prevention member 31 . The contact surface is a surface perpendicular to the axis X.

The sub-bearing 8 supports the drive shaft 6 along with the main bearing 7 on the axis X, and has an inner ring press-fitted to the drive shaft 6 and an outer ring press-fitted to the front housing 3 . The sub-bearing 8 is held on the axis X by the front housing 3 . The sub-bearing 8 is a needle bearing arranged closer to the scroll compression mechanism 5 than the lip seal 9 and having an outer diameter smaller than that of the main bearing 7 .

The lip seal 9 (seal portion) is a member that contacts the outer peripheral surface of the drive shaft 6 and prevents leakage of fluid along the drive shaft 6 . The lip seal 9 is attached to the inner peripheral surface of the front housing 3 and held on the axis X. As shown in FIG.

The retaining member 31 is an annular member attached to the end of the front housing 3 on the side of the scroll compression mechanism 5 while the main bearing 7 is press-fitted into the recess 3 a of the front housing 3 . The retaining member 31 is made of, for example, cast iron or steel.

An end surface of the retaining member 31 that contacts or approaches the front housing 3 is a retaining surface 31 a that is perpendicular to the axis X and contacts or approaches the contact surface of the main bearing 7 . The retaining surface 31a prevents the main bearing 7 from coming out of the recess 3a by coming into contact with or coming close to the contact surface of the main bearing 7. As shown in FIG.

As shown in FIG. 1, the end surface of the stopper member 31 on the side of the scroll compression mechanism 5 forms a sliding surface 31b that is perpendicular to the axis X and contacts or approaches the end surface 16a of the orbiting scroll 16 on the side of the front housing 3. there is For example, the sliding surface 31b is made of the material of the retaining member 31 (for example, cast iron or steel material). Further, for example, the sliding surface 31b is formed of a resin material such as PTFE (polytetrafluoroethylene) coated on the end surface of the removal prevention member 31 .

As shown in FIGS. 1 and 2, the retaining member 31 has a plurality of insertion holes 31c that open toward the scroll compression mechanism 5 and into which fastening bolts 40 for fastening the retaining member 31 to the front housing 3 are inserted. formed. As shown in FIG. 1 , the sliding surface 31 b of the retaining member 31 is arranged closer to the scroll compression mechanism 5 along the axis X than the head of the fastening bolt fastened to the front housing 3 .

The Oldham link 32 is a member that constitutes an anti-rotation mechanism that prevents the orbiting scroll 16 from rotating with respect to the crank pin 13 . As shown by phantom lines in FIG. 3, the Oldham link 32 includes a pair of protrusions 32a arranged on an axis Y orthogonal to the axis X, and a pair of protrusions 32a arranged on an axis Z orthogonal to the axes X and Y. and a protrusion 32b.

As shown in FIG. 2, the pair of protrusions 32a protrude toward the retaining member 31 and engage with a pair of grooves 31d formed in the retaining member 31 and extending in the direction of the axis Y. As shown in FIG. As shown in FIG. 1, the pair of projections 32b protrude toward the orbiting scroll 16 and engage with a pair of grooves 16b formed in the orbiting scroll 16 and extending in the direction of the axis Z. As shown in FIG.

Since the pair of protruding portions 32a of the Oldham link 32 are engaged with the pair of groove portions 31d of the retaining member 31, the moving direction of the Oldham link 32 is restricted so as to move only in the direction of the axis Y with respect to the retaining member 31. . In addition, since the pair of protrusions 32b of the Oldham link 32 are engaged with the pair of grooves 16b, the orbiting scroll 16 is limited in the movement direction so as to move only in the direction of the axis Z with respect to the Oldham link 32. . As a result, the movement of the orbiting scroll 16 with respect to the disengagement prevention member 31 is limited only in the direction of the combination of the movement in the direction of the axis line Y and the movement in the direction of the axis line Z, and rotation with respect to the crankpin 13 is prevented. .

Next, referring to FIG. 3, a mechanism for preventing the main bearing 7 from coming out of the recess 3a by the coming-off prevention member 31 will be described. As shown in FIG. 3, when assembling the open type compressor 1 of the present embodiment, the main bearing 7 is inserted into the recess 3a of the front housing 3 before attaching the retaining member 31 indicated by the phantom line to the front housing 3. is attached.

As shown in FIG. 3, the recess 3a of the front housing 3 has a cylindrical inner peripheral surface (first inner peripheral surface) 3c centered on the axis X and having a first diameter D1. The retaining member 31 has a cylindrical inner peripheral surface (second inner peripheral surface) 31e centered on the axis X and having a second diameter D2. The diameter of the outer peripheral surface 7d of the main bearing 7 is slightly larger than the first diameter D1 before being attached to the recess 3a. By press-fitting the main bearing 7 into the recess 3a, the third diameter D3 of the outer peripheral surface of the main bearing 7 becomes the same as the first diameter D1 of the inner peripheral surface 3c of the recess 3a.

After the main bearing 7 is press-fitted into the recess 3a, the retaining member 31 is attached at the position indicated by the phantom line in FIG. As shown in FIG. 3, the second diameter D2 of the retaining member 31 is smaller than the first diameter D1 of the inner peripheral surface 3c of the recess 3a and larger than the diameter of the outer peripheral surface of the inner ring 7a of the main bearing 7. . Also, the third diameter D3 of the outer peripheral surface 7d of the main bearing 7 is larger than the second diameter D2 of the retaining member 31 . As a result, the retaining surface 31a of the retaining member 31 comes into contact with the contact surface of the main bearing 7, thereby preventing the main bearing 7 from falling out of the recess 3a.

The operation and effects of the open type compressor 1 of this embodiment described above will be described.
According to the open type compressor 1 of this embodiment, the inner peripheral surface 31e of the retaining member 31 is larger than the first diameter D1 of the inner peripheral surface 3c of the recess 3a of the front housing 3 in which the main bearing 7 is held. The second diameter D2 is small. By making the second diameter D2 smaller than the first diameter D1, the diameters of the outer peripheral surface of the retaining member 31 and the outer peripheral surface of the front housing 3 can be reduced accordingly. Therefore, when the main bearing 7 is enlarged, it is possible to prevent the front housing 3 from being enlarged accordingly. Further, by making the second diameter D2 smaller than the first diameter D1, it is possible to increase the area of the thrust portion that supports the orbiting scroll 16, which is also used by the disengagement prevention member 31, thereby improving wear resistance. can do.

Further, the third diameter D3 of the outer peripheral surface 7d of the main bearing 7 is larger than the second diameter D2 of the inner peripheral surface 31e of the retaining member 31 . By making the third diameter D3 larger than the second diameter D2, the removal prevention member 31 prevents the main bearing 7 from coming off from the front housing 3 . Thus, according to the open type compressor 1 of the present embodiment, it is possible to hold the enlarged main bearing 7 inside without enlarging the front housing 3 that holds the main bearing 7 .

Further, according to the open type compressor 1 of the present embodiment, the retaining surface 31a of the retaining member 31 is brought into contact with the contact surface of the main bearing 7 on the side of the scroll compression mechanism 5, thereby allowing the main bearing 7 to move toward the front housing. 3 can be prevented. In addition, by bringing the slide surface 31b into contact with the end surface 16a of the orbiting scroll 16 on the front housing 3 side, the disengagement prevention member 31 can move the orbiting scroll 16 along the axis X of the drive shaft 6 without providing a separate thrust plate. It can be supported in the direction along (thrust direction).

Further, according to the open compressor 1 of the present embodiment, the sliding surface 31 b of the coming-off prevention member 31 is arranged closer to the scroll compression mechanism 5 than the head of the fastening bolt 40 . Therefore, the retaining bolt 40 is used to fasten the retaining member 31 to the front housing 3, and the sliding surface 31b of the retaining member 31 is used to move the orbiting scroll 16 in the direction along the axis X of the drive shaft 6 (thrust direction). ).

[Second embodiment]
Next, an open type compressor 1A according to a second embodiment of the present invention will be described with reference to the drawings. This embodiment is a modified example of the first embodiment, and is assumed to be the same as the first embodiment except for the case where it will be particularly described below, and the description below will be omitted.

The open compressor 1 of the first embodiment uses the Oldham link 32 as a rotation prevention mechanism that prevents the orbiting scroll 16 from rotating with respect to the crankpin 13 . On the other hand, in the open compressor 1A of this embodiment, the anti-rotation pin 50 attached to the orbiting scroll 16 and the anti-rotation hole 31f formed in the prevention member 31 function as an anti-rotation mechanism.

FIG. 4 is a longitudinal sectional view showing an open compressor 1A of this embodiment. 5 is a view of the front housing 3 and the retaining member 31 of the open compressor 1A shown in FIG. 4 as viewed along the axis X of the drive shaft 6. FIG. 5 is a view of the open compressor 1A viewed from the direction of arrow I in FIG. 4, showing a state in which the scroll compression mechanism 5 and the rear housing 2 are removed. The vertical cross-sectional view shown in FIG. 4 is a cross-sectional view taken along line BB in FIG.

As shown in FIG. 4, a plurality of anti-rotation pins 50 protruding along the axis X are attached to the end of the orbiting scroll 16 on the front housing 3 side. The anti-rotation pin 50 is, for example, a cylindrical member made of cast iron or steel. As indicated by phantom lines in FIG. 5 , the anti-rotation pins 50 are attached to the orbiting scroll 16 at four locations around the center axis of the crankpin 13 at intervals of 90 degrees.

As shown in FIG. 4, a plurality of rotation-preventing holes 31f having cylindrical inner peripheral surfaces for accommodating the tips of the rotation-preventing pins 50 are formed in the end face of the disengagement-preventing member 31 on the orbiting scroll 16 side. ing. The anti-rotation hole 31f has an inner diameter larger than the outer diameter of the anti-rotation pin 50, and has a circular cross-sectional shape perpendicular to the axis X. As shown in FIG. As shown in FIG. 5, the anti-rotation holes 31f are formed around the axis X at four locations on the retaining member 31 at intervals of 90 degrees.

As shown in FIG. 4, when the sliding surface 31b of the retaining member 31 and the end surface 16a of the orbiting scroll 16 are in contact with each other, the tip of the anti-rotation pin 50 is inserted into the anti-rotation hole 31f. Therefore, the movement range of the anti-rotation pin 50 is restricted by the anti-rotation hole 31f. As a result, the movement of the orbiting scroll 16 is restricted to the range of the rotation prevention hole 31f, and rotation with respect to the crankpin 13 is prevented.

As shown in FIG. 4, the diameter of the inner peripheral surface 31e of the detachment prevention member 31 of the present embodiment is the second diameter D2 on the detachment prevention member 31 side, which is the same as in the first embodiment, while the diameter on the orbiting scroll 16 side is D2. A fourth diameter D4 is smaller than the second diameter D2. This is because the anti-rotation pin 50 and the anti-rotation hole 31f are employed as the anti-rotation mechanism instead of the Oldham link 32 of the first embodiment. This is because By setting the fourth diameter D4 smaller than the second diameter D2 on the orbiting scroll 16 side, the contact area between the end surface 16a of the orbiting scroll 16 and the sliding surface 31b of the retaining member 31 is increased, and the thrust force of the orbiting scroll 16 is increased. The removal prevention member 31 can support more securely.

According to the open type compressor 1A of the present embodiment described above, by inserting the plurality of rotation prevention pins 50 attached to the orbiting scroll 16 into the plurality of rotation prevention holes 31f formed in the removal prevention member 31, the The scroll 16 is prevented from rotating with respect to the crankpin 13, and the fluid can be properly compressed by the compression chamber.

[Third embodiment]
Next, an open type compressor 1B according to a third embodiment of the present invention will be described with reference to the drawings. This embodiment is a modified example of the first embodiment, and is assumed to be the same as the first embodiment except for the case where it will be particularly described below, and the description below will be omitted.

The open compressor 1 of the first embodiment uses the Oldham link 32 as a rotation prevention mechanism that prevents the orbiting scroll 16 from rotating with respect to the crankpin 13 . On the other hand, in the open compressor 1B of the present embodiment, the anti-rotation pin 60 attached to the coming-off prevention member 31 and the anti-rotation hole 16c formed in the orbiting scroll 16 function as an anti-rotation mechanism.

FIG. 6 is a longitudinal sectional view showing an open compressor 1B of this embodiment. 7 is a view of the front housing 3 and the retaining member 31 of the open compressor 1B shown in FIG. 6 as viewed along the axis X of the drive shaft 6. FIG. 7 is a view of the open compressor 1B viewed from the direction of arrow J in FIG. 6, showing a state in which the scroll compression mechanism 5 and the rear housing 2 are removed. The vertical cross-sectional view shown in FIG. 6 is a cross-sectional view taken along line C--X--C in FIG.

As shown in FIG. 6, a plurality of anti-rotation pins 60 protruding along the axis X are attached to the end of the anti-disengagement member 31 on the orbiting scroll 16 side. The anti-rotation pin 60 is, for example, a cylindrical member made of cast iron or steel. As shown in FIG. 7, the anti-rotation pins 60 are attached to four locations of the slip-off prevention member 31 around the axis X at intervals of 90 degrees.

As shown in FIG. 6, the end face 16a of the orbiting scroll 16 on the side of the anti-removal member 31 is formed with a plurality of anti-rotation holes 16c each having a cylindrical inner peripheral surface for accommodating the tips of the anti-rotation pins 60. It is The anti-rotation hole 16c has an inner diameter larger than the outer diameter of the anti-rotation pin 60, and has a circular cross-sectional shape perpendicular to the axis X. As shown in FIG. As indicated by phantom lines in FIG. 7, the rotation prevention holes 16c are formed at four locations on the orbiting scroll 16 around the axis X at intervals of 90 degrees.

A protective ring (annular member) 16d having an annular cross-section orthogonal to the axis X is held on the inner peripheral surface of the rotation prevention hole 16c of the orbiting scroll 16 . The protection ring 16d is made of, for example, cast iron or steel. On the other hand, the orbiting scroll 16 is made of aluminum or aluminum alloy. The protection ring 16d protects the anti-rotation pin 60 made of cast iron or steel from coming into contact with the orbiting scroll 16 made of aluminum or an aluminum alloy, thereby preventing the anti-rotation hole 16c of the orbiting scroll 16 from wearing. be.

As shown in FIG. 6, when the sliding surface 31b of the removal prevention member 31 and the end surface 16a of the orbiting scroll 16 are in contact with or close to each other, the tip of the rotation prevention pin 60 is inserted into the rotation prevention hole 16c. Become. Therefore, the movement range of the anti-rotation pin 60 is restricted by the anti-rotation hole 16c. As a result, the movement of the orbiting scroll 16 is restricted to the range of the anti-rotation hole 16c, and rotation with respect to the crankpin 13 is prevented.

As shown in FIG. 6, the diameter of the inner peripheral surface 31e of the detachment prevention member 31 of the present embodiment is the second diameter D2 on the detachment prevention member 31 side, which is the same as in the first embodiment, while the diameter on the orbiting scroll 16 side is D2. A fourth diameter D4 is smaller than the second diameter D2. Since the rotation prevention pin 60 and the rotation prevention hole 16c are employed as the rotation prevention mechanism in place of the Oldham link 32 of the first embodiment, the area where the Oldham link 32 was present is replaced by the area where the removal prevention member 31 is present. This is because By setting the fourth diameter D4 smaller than the second diameter D2 on the orbiting scroll 16 side, the contact area between the end surface 16a of the orbiting scroll 16 and the sliding surface 31b of the retaining member 31 is increased, and the thrust force of the orbiting scroll 16 is increased. The removal prevention member 31 can support more securely.

Next, a mechanism for positioning the front housing 3 and the retaining member 31 so that they are arranged on the same axis X when attaching the retaining member 31 to the front housing 3 will be described. This positioning mechanism is composed of a first positioning hole 3 e formed in the front housing 3 and a second positioning hole 31 h formed in the retaining member 31 .

As shown in FIG. 6, a first positioning hole 3e extending along the axis X is formed in a mounting surface (first mounting surface) 3d of the front housing 3 to which the retaining member 31 is mounted. As shown in FIG. 7, the first positioning holes 3e are bottomed holes having a circular cross section orthogonal to the axis X, and are formed at two locations around the axis X at intervals of 180 degrees. A positioning pin (bar-shaped member) 70 having a diameter substantially equal to the diameter of the hole and having a circular cross section can be inserted into the first positioning hole 3e.

As shown in FIG. 6, a second positioning hole 31h extending along the axis X is formed in an attachment surface (second attachment surface) 31g of the retaining member 31 attached to the front housing 3. As shown in FIG. As shown in FIG. 6, the second positioning holes 31h are bottomed holes having a circular cross section perpendicular to the axis X, and are formed at two locations around the axis X at intervals of 180 degrees. A positioning pin 70 can be inserted into the second positioning hole 31h.

An operator who assembles the open compressor 1B inserts the positioning pin 70 into each of the two first positioning holes 3e before attaching the retaining member 31 to the front housing 3. As shown in FIG. Thereafter, the operator performs alignment work so that the positioning pin 70 protruding from the mounting surface 3 d is inserted into the second positioning hole 31 h of the retaining member 31 . With the positioning pin 70 inserted into both the first positioning hole 3e and the second positioning hole 31h, the operator inserts the fastening bolt 40 into the insertion hole 31c to fix the retaining member 31 to the front housing 3. . As a result, assembly workability can be improved, and positional deviation in the rotational direction during use can be further prevented.

According to the open compressor 1B of the present embodiment described above, by inserting the plurality of rotation prevention pins 60 attached to the disengagement prevention member 31 into the plurality of rotation prevention holes 16c formed in the orbiting scroll 16, the orbiting The scroll 16 is prevented from rotating with respect to the crankpin 13, and the fluid can be properly compressed by the compression chamber.

Further, according to the open compressor 1B of this embodiment, one end of the positioning pin 70 is inserted into the first positioning hole 3e formed in the mounting surface 3d of the front housing 3, The retaining member 31 is positioned with respect to the front housing 3 by inserting the other end of the positioning pin 70 into the formed second positioning hole 31h. Therefore, the retaining member 31 can be fixed to the front housing 3 while the retaining member 31 is positioned with respect to the front housing 3 .

In the present embodiment, the second positioning hole 31h formed in the removal prevention member 31 is a bottomed hole, but it may be a through hole. In this case, the positioning pin 70 may have a length protruding from the second positioning hole 31h, and the positioning pin 70 may be pulled out after the retaining member 31 is fixed to the front housing 3. FIG. By doing so, the positioning pin 70 used for positioning can be removed from the final product.

1, 1A, 1B open compressor 2 rear housing (first housing)
3 Front housing (second housing)
3a recess 3b recess 3c inner peripheral surface (first inner peripheral surface)
3d mounting surface (first mounting surface)
3e First positioning hole 5 Scroll compression mechanism 6 Drive shaft 7 Main bearing (bearing portion)
7a inner ring 7b outer ring 7d outer peripheral surface 13 crankpin 15 fixed scroll 16 orbiting scroll 16a end surface 16b groove 16c rotation prevention hole 16d protection ring (annular member)
31 retaining member 31a retaining surface 31b sliding surface 31c insertion hole 31d groove 31e inner peripheral surface (second inner peripheral surface)
31f rotation prevention hole 31g mounting surface (second mounting surface)
31h Second positioning hole 32 Oldham link (anti-rotation mechanism)
40 fastening bolt 50 anti-rotation pin 60 anti-rotation pin 70 positioning pin D1 first diameter D2 second diameter D3 third diameter IN inlet X, Y, Z axis

Claims (7)

a compression mechanism that is driven by a drive shaft that rotates about an axis and that compresses a fluid that flows in from an inlet and discharges the fluid from an outlet;
a bearing that supports the drive shaft;
a first housing that accommodates the compression mechanism and is formed in a cylindrical shape;
a second housing which is attached to close the opening of the first housing and has a recess formed in the end on the side of the compression mechanism for holding the bearing on the axis;
a removal prevention member attached to the end of the second housing on the side of the compression mechanism in a state where the bearing portion is held in the recess;
the recess comprises a cylindrical first inner peripheral surface having a first diameter centered on the axis;
The disengagement prevention member has a cylindrical second inner peripheral surface having a second diameter smaller than the first diameter centered on the axis,
The bearing portion has a cylindrical outer peripheral surface having a third diameter larger than the second diameter,
The compression mechanism has a fixed scroll fixed to the first housing and an orbiting scroll connected to a crank pin eccentric to the drive shaft, and the orbiting scroll meshed with the fixed scroll. It is a mechanism that compresses the fluid by driving it to revolve,
a rotation prevention mechanism that prevents the orbiting scroll from rotating with respect to the crankpin;
The anti-rotation mechanism is
a plurality of anti-rotation pins attached to the second housing side end of the orbiting scroll and protruding along the axis;
an open type compressor comprising a plurality of anti-rotation holes formed in the anti-disengagement member and having a cylindrical inner peripheral surface for accommodating the tips of the anti-rotation pins. a compression mechanism that is driven by a drive shaft that rotates about an axis and that compresses a fluid that flows in from an inlet and discharges the fluid from an outlet;
a bearing that supports the drive shaft;
a first housing that accommodates the compression mechanism and is formed in a cylindrical shape;
a second housing which is attached to close the opening of the first housing and has a recess formed in the end on the side of the compression mechanism for holding the bearing on the axis;
a removal prevention member attached to the end of the second housing on the side of the compression mechanism in a state where the bearing portion is held in the recess;
the recess comprises a cylindrical first inner peripheral surface having a first diameter centered on the axis;
The disengagement prevention member has a cylindrical second inner peripheral surface having a second diameter smaller than the first diameter centered on the axis,
The bearing portion has a cylindrical outer peripheral surface having a third diameter larger than the second diameter,
The compression mechanism has a fixed scroll fixed to the first housing and an orbiting scroll connected to a crank pin eccentric to the drive shaft, and the orbiting scroll meshed with the fixed scroll. It is a mechanism that compresses the fluid by driving it to revolve,
a rotation prevention mechanism that prevents the orbiting scroll from rotating with respect to the crankpin;
The anti-rotation mechanism is
a plurality of anti-rotation pins attached to the orbiting scroll-side end of the disengagement prevention member and protruding along the axis;
an open type compressor comprising a plurality of anti-rotation holes formed in the orbiting scroll and having a cylindrical inner peripheral surface for accommodating the tips of the anti-rotation pins. The orbiting scroll is made of an aluminum alloy,
The anti-rotation pin is made of cast iron or steel,
3. The open type compressor according to claim 2 , wherein the anti-rotation mechanism has an annular member held on the inner peripheral surface of the anti-rotation hole and made of cast iron or steel. A first mounting surface of the second housing to which the removal prevention member is mounted is formed with a first positioning hole into which a rod-shaped member extending along the axis and having a circular cross section can be inserted,
4. The second positioning hole into which the rod-shaped member can be inserted is formed in the second mounting surface of the retaining member mounted on the second housing. Open type compressor. a compression mechanism that is driven by a drive shaft that rotates about an axis and that compresses a fluid that flows in from an inlet and discharges the fluid from an outlet;
a bearing that supports the drive shaft;
a first housing that accommodates the compression mechanism and is formed in a cylindrical shape;
a second housing which is attached to close the opening of the first housing and has a recess formed in the end on the side of the compression mechanism for holding the bearing on the axis;
a removal prevention member attached to the end of the second housing on the side of the compression mechanism in a state where the bearing portion is held in the recess;
the recess comprises a cylindrical first inner peripheral surface having a first diameter centered on the axis;
The disengagement prevention member has a cylindrical second inner peripheral surface having a second diameter smaller than the first diameter centered on the axis,
The bearing portion has a cylindrical outer peripheral surface having a third diameter larger than the second diameter,
The compression mechanism has a fixed scroll fixed to the first housing and an orbiting scroll connected to a crank pin eccentric to the drive shaft, and the orbiting scroll meshed with the fixed scroll. It is a mechanism that compresses the fluid by driving it to revolve,
a rotation prevention mechanism that prevents the orbiting scroll from rotating with respect to the crankpin;
The coming-off prevention member is
a retainer surface orthogonal to the axis and in contact with or close to the contact surface of the bearing portion on the compression mechanism side;
an open type compressor having a sliding surface orthogonal to the axis and in contact with or in close proximity to the end surface of the orbiting scroll on the side of the second housing. The removal prevention member is formed with an insertion hole that opens toward the compression mechanism and into which a fastening bolt that fastens the removal prevention member to the second housing is inserted,
6. The open type compressor according to claim 5 , wherein the sliding surface is arranged closer to the compression mechanism along the axis than the head of the fastening bolt. 4. The open compressor according to claim 3 , wherein said retaining member is made of cast iron or steel.

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