JPH07158571A - Scroll type compressor - Google Patents

Abstract

PURPOSE:To prevent the increase of the physical size of a compressor and the increase of a manufacturing cost and to perform cooling and lubrication of a shaft sealing device with the low suction resistance. CONSTITUTION:The communication port 62d of a suction passage 62b is opened to the radiation position of a fixed vortex substance 23 and a moving vortex substance 42. A shaft sealing device 31 is communicated with a compression chamber 1b on the outer wall side before sealing through a refrigerant passage 62c. An inner end face 30b to ensure a gap C communicated with the shaft sealing device 31 and cross a drive shaft 33 at right angles is formed at a front housing 30. A slinger 33b synchronously rotated facing the inner end face 30b and radially outwardly moving refrigerant gas to a low pressure area by means of viscosity and the centrifugal force of included refrigerant gas is arranged on the drive shaft 33.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a scroll compressor.

[0002]

2. Description of the Related Art As a conventional scroll type compressor (hereinafter, simply referred to as a compressor), a compressor described in Japanese Utility Model Publication No. 63-43424 is known. In this compressor, the front housing, the front end plate, and the rear housing form an outer shape as a housing. A suction port and a discharge port are formed in the rear housing, and a fixed scroll including a fixed side plate and a fixed scroll is fixed. A movable scroll composed of a movable side plate and a movable scroll body is meshed with the fixed scroll in the rear housing while being 180 ° out of phase with each other, thereby forming an inner wall side compression chamber on the inner wall side of the movable scroll body.
An outer wall side compression chamber is formed on the outer wall side of the movable scroll.
A drive shaft is rotatably supported on the front end plate via a shaft sealing device and a bearing, and a drive pin is provided at a rear end of the drive shaft so as to project therefrom. A drive bush for revolving the movable scroll via a radial bearing is fitted to the drive pin, and a rotation preventing mechanism for preventing rotation of the movable scroll is provided between the front end plate and the movable side plate of the movable scroll. There is. Further, in this compressor, the rear housing is provided with a main suction passage that communicates with the inner wall side compression chamber and the outer wall side compression chamber before being sealed from the suction port at one end by the communication port at the other end. As such a configuration, the front end plate and the rear housing are provided with an auxiliary suction passage branched from the main suction passage to reach the shaft sealing device.

In this compressor, when the drive shaft is rotationally driven, the drive bush is driven by the drive pin to rotate. The rotation of the drive bush is transmitted to the movable scroll via the radial bearing, and the movable scroll is prevented from rotating by the rotation preventing mechanism, so that the movable scroll executes only the revolution movement. As a result, the inner wall side compression chamber and the outer wall side compression chamber are sequentially moved from the outermost side toward the center of the spiral to be sealed, and then the volume is reduced to form a single compression chamber, whereby the refrigerant gas sucked from the suction port is drawn. And is discharged from the discharge port.

During this period, according to the above publication, a part of the refrigerant gas sucked from the suction port through the main suction passage can be introduced into the shaft sealing device through the auxiliary suction passage. It is possible that the refrigerant is cooled by the refrigerant gas itself and is lubricated with a mist-like lubricating oil contained in the refrigerant gas, and then the bearings and the like are also lubricated.

[0005]

However, in the above-mentioned conventional compressor, the suction port and the shaft sealing device are merely connected by the auxiliary suction passage. Therefore, even if the refrigerant gas reaches the shaft sealing device, the refrigerant gas reaches the inner wall side compression chamber and the outer wall side compression chamber before being sealed at the suction execution stage through the gap between the rolling elements of the bearing. The suction resistance after the shaft sealing device is increased. Further, almost no differential pressure is generated between the vicinity of the suction port, the shaft sealing device, and the inner wall side compression chamber and the outer wall side compression chamber before being sealed. In this way, the refrigerant gas is mostly supplied to the inner wall side compression chamber and the outer wall side compression chamber via the shaft sealing device, the bearing, etc., due to the high suction resistance and almost no differential pressure. Instead, it is supplied to the inner wall side compression chamber and the outer wall side compression chamber by the main suction passage. Therefore, in this compressor,
Cooling and lubrication of the shaft seal device may be insufficient, and lubrication of the bearing and the like may be insufficient.

On the other hand, if the communication port of the main suction passage is opened between the shaft sealing device and the bearing in order to sufficiently cool and lubricate the shaft sealing device, the refrigerant gas is allowed to flow between the rolling elements of the bearing. It is necessary to reach the inner wall side compression chamber and the outer wall side compression chamber before being sealed, which is the stage of performing suction through a gap or the like, and suction resistance increases, resulting in a reduction in compression efficiency.

Further, Japanese Utility Model Laid-Open No. 60-170088,
Japanese Utility Model Laid-Open No. Sho 62-132287 and Japanese Patent Laid-Open No. 2771/1990.
Japanese Unexamined Patent Publication No. 86 discloses a compressor including an oil separator, a pump and the like capable of supplying lubricating oil to a shaft sealing device and the like. However, in these compressors, by incorporating an oil separator, a pump, etc., the physique becomes larger and the mountability on a vehicle etc. is impaired, and the manufacturing cost rises. .

An object of the present invention is to sufficiently cool and lubricate a shaft seal device without increasing the size of the compressor and increasing the manufacturing cost, and under a low suction resistance.

[0009]

[Means for Solving the Problems]

(1) In order to solve the above-mentioned problems, the compressor of the present invention is installed in a housing having an intake passage having an intake port and a communication port opened therein, and in a low pressure region in the housing which communicates with the communication port. A bearing, a drive shaft sealed in the housing by a shaft sealing device and supported by the housing via the bearing, and a fixed scroll fixed to the housing with a fixed side plate and a fixed scroll. A movable side plate and a movable scroll body housed in the housing and meshing with the fixed scroll are provided, and an inner wall side compression chamber communicating with the communication port through the low pressure region is formed on the inner wall side of the movable scroll body. ,
A movable scroll that forms an outer wall side compression chamber that communicates with the communication port through the low pressure region on the outer wall side of the movable scroll, and a drive pin that is projectingly provided at the rear end of the drive shaft, and is a radial bearing. A movable bush for revolving the orbiting scroll via a rotor, and a rotation preventing mechanism for preventing the orbiting of the orbiting scroll from engaging with the housing and the orienting side plate of the orbiting scroll in the low pressure region. The inner wall side compression chamber and the outer wall side compression chamber are successively moved toward the center of the vortex to be hermetically closed by the orbital movement of the above, and then the volume is reduced to form a single compression chamber. In the scroll compressor for compressing and discharging the refrigerant gas, the communication port is opened at the radial position of the fixed scroll and the movable scroll, and the inner wall side before being sealed with the shaft sealing device. At least one of the compression chamber and the compression chamber on the outer wall side is communicated with a refrigerant passage, and an inner end surface orthogonal to the drive shaft is formed in the housing with a gap communicating with the shaft sealing device being formed. Is provided with a slinger that rotates in synchronism with the inner end face and that moves the refrigerant gas radially outward by the viscosity and centrifugal force of the interposed refrigerant gas to reach the low pressure region. Taking new steps.

(2) In the compressor of the present invention, the slinger may have a guide groove or a guide projection formed radially on the inner end face side. (3) Further, in the compressor of the present invention, it is preferable that the slinger is formed integrally with the drive shaft.

[0011]

[Action]

(1) In the compressor of claim 1, the outermost inner wall side compression chamber and the outermost wall side compression chamber have a pressure lower than the pressure of the suction port before being sealed at the suction execution stage. Then, in the suction passage having the suction port opened at one end, the communication port at the other end is opened at the radial positions of the fixed scroll and the movable scroll. For this reason, the refrigerant gas near the suction port reaches the outermost inner wall side compression chamber and the outermost wall side compression chamber under the low suction resistance due to the suction passage.

When the drive shaft rotates, the slinger rotates synchronously. At this time, since the slinger faces the inner end surface formed in the housing at a right angle to the drive shaft,
The refrigerant gas interposed between the inner end surface and the slinger is moved radially outward due to its viscosity and centrifugal force. Since the inner end face has a gap communicating with the shaft sealing device, the gap becomes negative pressure as the refrigerant gas moves radially outward. When the gap becomes negative pressure in this way, the refrigerant gas is moved to the gap from at least one of the inner wall side compression chamber and the outer wall side compression chamber before being sealed through the refrigerant passage. Therefore, the refrigerant gas is supplied to the shaft sealing device.

The refrigerant gas supplied to the shaft sealing device cools the shaft sealing device by the refrigerant gas itself and lubricates with the mist-like lubricating oil contained in the refrigerant gas. Then, since the outermost inner wall side compression chamber and the outermost wall side compression chamber are at a pressure lower than the pressure of the suction port, the refrigerant gas reaches a low pressure region through a bearing or the like, and then the inner wall side before being sealed. Since it is sucked into the compression chamber and the compression chamber on the outer wall side, it also lubricates the bearings and the like.

(2) In the compressor of the second aspect, the slinger rotates in synchronization with the drive shaft, so that the refrigerant gas interposed between the inner end surface and the slinger is guided in a guide groove or guide formed in the radial direction. Since it is guided by the convex portion, it is positively moved in the radial direction due to its viscosity and centrifugal force. (3) In the compressor of claim 3, since the slinger is formed integrally with the drive shaft, the slinger can be used as a bearing holding flange.

[0015]

【Example】

(Embodiment 1) Hereinafter, Embodiment 1 which embodies the compressor of claims 1 and 3 will be described with reference to the drawings. This compressor is
As shown in FIG. 1, the fixed side plate 21 and the fixed side plate 21
A fixed scroll 2 composed of a shell portion 22 integrally formed with the movable side plate 21 and an outer shell, and a fixed scroll 23 formed by an involute curve or the like inside the fixed side plate 21 includes a movable side plate 41 and an inner side of the movable side plate 41. The compression chamber 1 is formed by meshing with the movable scroll 4 composed of the movable scroll 42 formed by an involute curve or the like.

That is, as shown in FIG. 2, the inner wall of the movable scroll 42 and the outer wall of the fixed scroll 23 constitute the inner wall side compression chamber 1a, and the outer wall of the movable scroll 42 is fixed.
The outer wall side compression chamber 1b is configured together with the inner wall 3 of FIG. The shell portion 22 of the fixed scroll 2 is, as shown in FIG.
The front housing 30 and the rear housing 38 are fastened with through bolts 3 (see FIG. 2), and the drive shaft 3 is inserted into the boss of the front housing 30 via a shaft sealing device 31.
3 has been extended.

Behind the drive shaft 33, a flat disk-shaped slinger 33b is the most characteristic structure of the compressor.
Are integrally formed. Further, as shown in FIG. 3, the front housing 30 has an inner end surface 30b which is orthogonal to the drive shaft 33 while ensuring a gap C communicating with the shaft sealing device 31.
Are formed. The slinger 33b has the inner end surface 3
They are faced with each other while ensuring a distance l of 0 mm or less and about 0.1 mm or less.

Behind the slinger 33b, as shown in FIG. 1, a large diameter portion 33a having a diameter slightly smaller than that of the slinger 33b.
Is also integrally formed, and the rear surface of the slinger 33b is used as a bearing pressing flange between the front housing 30 and the large diameter portion 33a to form the angular contact ball bearing 32.
Is intervening. Further, as shown in FIG. 2, the shaft sealing device 31 and the outermost outer wall side compression chamber 1b before being sealed are communicated by a refrigerant passage 62c and a gap C as shown in FIG. ing.

As shown in FIG. 2, the suction flange 62 is provided on the shell portion 22 and the front housing 30.
Are formed. The suction flange 62 is formed with a suction passage 62b having a suction port 62a connected to the external refrigeration circuit at one end and a communication port 62d at the other end located at the radial position of the fixed scroll 23 and the movable scroll 42. There is. The communication port 62d communicates with the ends of the spiral groove formed by the inner wall of the shell 22 and the inner and outer walls of the fixed spiral body 23, whereby the suction port 62a is the outermost inner wall compression chamber 1a and outer wall compression chamber 1b. It is possible to communicate with. This communication port 62d
As shown in FIG. 1, is communicated with a gap that allows the orbiting of the movable scroll 4 and a gap of a rotation prevention mechanism described later, and these gaps are a low pressure region that communicates with the bearing 32.

A drive pin 34 is provided at the rear end of the large diameter portion 33a of the drive shaft 33 so as to project therefrom. A counterweight 35 and a drive bush 36 are fitted to the drive pin 34, and a boss of a movable side plate 41 is supported by the drive bush 36 via a radial bearing 37. The drive pin 34
Has a drive surface 34a inclined rearward in the rotational direction of the drive shaft 33, and the drive bush 36 can be guided in the radial direction along the drive surface 34a.

Further, a movable ring 51 having a predetermined number of rotation preventing pins 51a extending in the axial direction is interposed between the front housing 30 and the movable side plate 41, and the rotation preventing pins 51a are recessed in the front housing 30. The regulated hole 30a and the regulated hole 41a recessed in the movable side plate 41 are engaged with each other through steel liners, whereby the radial force acting from the drive shaft 33 and the movable side plate 41 is received. The side plate 41 is prevented from rotating. The front and rear surfaces of the movable ring 51 provided with the rotation prevention pin 51a have a gap of several tens of μm between the front housing 30 and the movable side plate 41 in order to appropriately receive the radial force. . On the other hand, the front and rear surfaces of the movable ring 51, which is not provided with the rotation prevention pin 51a, slidably abuts on the front housing 30 and the movable side plate 41, whereby the thrust force acting from the movable side plate 41 is received. ing. A rotation prevention mechanism is configured by the rotation prevention pin 51a, the movable ring 51, and the restriction holes 30a and 41a.

Further, the discharge chamber 3 is provided in the rear housing 38.
9 is formed, and the discharge chamber 39 is communicated with the discharge port 2 penetrating the central portion of the fixed side plate 21 through the discharge valve mechanism 6, and is also communicated with the refrigeration circuit through a discharge port (not shown). ing. In the compressor configured as described above, when the drive shaft 33 is rotationally driven by the electromagnetic clutch, the drive bush 36 is driven by the drive pin 34 to rotate. The rotation of the drive bush 36 depends on the radial bearing 3
7 is transmitted to the movable side plate 41, and the movable side plate 41 is rotated by the rotation preventing pin 51a, the movable ring 51, and the restriction hole 30a.
Since the rotation of the movable scroll 4 is prevented by 41a, the movable scroll 4 executes only the revolution movement along the revolution circle. As a result, the fixed side plate 21, the fixed scroll 23, the movable side plate 4
1 and an inner wall side compression chamber 1 formed by the movable scroll 42
The a and the outer wall side compression chamber 1b are sequentially moved from the outermost side toward the center of the spiral to be sealed, and then are moved toward the center of the spiral while reducing the volume.

In the meantime, the outermost inner wall side compression chamber 1a and the outermost wall side compression chamber 1b are at a pressure lower than the pressure of the suction port 62a. As shown in FIG. 2, the suction passage 62b having the suction port 62a opened at one end has the communication port 62d at the other end opened at the radial positions of the fixed scroll 23 and the movable scroll 42. Therefore, the refrigerant gas near the suction port 62a reaches the outermost inner wall side compression chamber 1a and the outermost wall side compression chamber 1b under a low suction resistance due to the suction passage 62b.

When the drive shaft 33 rotates, the slinger 33b rotates synchronously. At this time, since the slinger 33b faces the inner end surface 30b with a distance 1 of about 0.1 mm or less secured, the inner end surface 30b and the slinger 33b face each other.
The refrigerant gas interposed between and is moved radially outward due to its viscosity and centrifugal force. That is, as shown in FIG. 4, in synchronization with the drive shaft 33, the slinger 33 b moves the angular velocity ω
When rotated by, the velocity v at the position A separated from the axis O by the radius r has a magnitude of rω at right angles to the OA and in the rotation direction. This velocity v has the distribution shown in FIG. 5 between the front surface of the slinger 33b and the inner end surface 30b. The refrigerant gas tends to move to the position B according to the area where the velocity v is distributed. As shown in FIG. 4, by moving from the position A to the position B, the radius is Δ from the position A ′ after the position A is rotated.
Since it has increased by r, the refrigerant gas is moved radially outward by Δr. Note that, in reality, since it is viscous, the refrigerant gas moves in the radial direction on the front side of the slinger 33b by a distance slightly smaller than Δr.

Since the inner end surface 30b secures the gap C communicating with the shaft sealing device 31, the gap C becomes negative pressure when the refrigerant gas moves radially outward. When the gap C becomes negative pressure in this way, the refrigerant gas is moved to the gap C from the outer wall side compression chamber 1b before being sealed through the refrigerant passage 62c. Therefore, the refrigerant gas is supplied to the shaft sealing device 31.

The refrigerant gas guided to the shaft sealing device 31 cools the shaft sealing device 31 by the refrigerant gas itself and lubricates with the mist-like lubricating oil contained in the refrigerant gas.
After that, the outermost inner wall side compression chamber 1a and the outermost wall side compression chamber 1b
Since the pressure of the refrigerant gas is lower than the pressure of the suction port 62a, the refrigerant gas reaches the low pressure region through the gap between the rolling elements of the bearing 32 and the like, and is then compressed to the inner wall side compression chamber 1a and the outer wall side compression chamber 1a before being sealed. Since it is sucked into the chamber 1b, it also lubricates the bearing 32 and the like. This flow is shown by an arrow in FIG.

In this way, the inner wall side compression chamber 1a and the outer wall side compression chamber 1b are sequentially moved from the outermost side toward the center of the spiral to be sealed, and then the volume is reduced to a single compression chamber 1c, whereby the suction is performed. The refrigerant gas sucked from the opening 62 a is discharged through the discharge port 2 and the discharge valve mechanism 3 to the discharge chamber 39.
And is circulated from the discharge port to the external refrigeration circuit. Therefore, in this compressor, since the refrigerant gas can be easily supplied to the shaft sealing device 31, the shaft sealing device 31 can be sufficiently cooled and lubricated. Therefore, this compressor can exhibit excellent durability.

Further, in this compressor, since the suction resistance hardly increases due to the lubrication of the shaft sealing device 31 and the like, a high compression efficiency can be maintained. further,
In order to achieve this effect, this compressor does not have a conventional oil separator, pump, etc. built-in, so it is possible to avoid an increase in body size and exhibit excellent mountability on vehicles, etc. The manufacturing cost can be reduced.

Further, in this compressor, since the lubricating oil in the compressed refrigerant gas is not supplied to the shaft seal device 31, the refrigerant gas is not reexpanded and recompressed, and high compression efficiency is maintained. can do. In addition, in this compressor, since the passage area of the suction passage 62b is not reduced, suction resistance due to the suction passage 62b does not increase, and high compression efficiency can be ensured.

In this compressor, since the slinger 33b is formed integrally with the drive shaft 33, it can be manufactured at low cost. (Embodiment 2) The compressor according to Embodiment 2 is a concrete embodiment of the compressor according to Claims 1 and 2. As shown in FIG. 6, this compressor has a guide groove 61 in the radial direction on the front surface of the slinger 61.
a is recessed. The slinger 61 is fixed to the drive shaft 33 by a key (not shown). Since the other points are the same as those of the first embodiment, the same components are designated by the same reference numerals, and the description of the same operation and effect will be omitted.

In this compressor, the slinger 61 rotates synchronously with the drive shaft 33, so that the refrigerant gas interposed between the inner end surface 30b and the slinger 61 is guided by the guide groove 61a formed in the radial direction. Therefore, even if the distance 1 between the inner end surface 30b and the slinger 61 is slightly larger than about 0.1 mm, it is positively moved radially outward due to its viscosity and centrifugal force.

Therefore, in this compressor, the shaft sealing device 3
Since the refrigerant gas can be more easily supplied to 1,
It is possible to sufficiently cool and lubricate the shaft sealing device 31,
As a result, more excellent compression efficiency and durability can be exhibited. (Embodiment 3) The compressor of the embodiment 3 also embodies the compressors of claims 1 and 2.

In this compressor, as shown in FIG. 7, a slinger 62 is provided with a guide projection 62a on the front surface in a radial direction. Since the other points are the same as those of the second embodiment, the same reference numerals are given to the same configurations, and the description of the same operation and effect is omitted. In this compressor, since the slinger 62 rotates synchronously with the drive shaft 33, the refrigerant gas interposed between the inner end surface 30b and the slinger 62 is guided by the guide convex portion 62a formed in the radial direction. The same operation and effect as those of the second embodiment can be obtained.

[0034]

As described above in detail, since the compressor of the present invention employs the structure described in the claims, the refrigerant gas can be easily supplied to the shaft sealing device under a low suction resistance. Therefore, the shaft seal device can be sufficiently cooled and lubricated under high compression efficiency. Therefore, this compressor can exhibit excellent compression efficiency and durability.

Further, in this compressor, in order to exert such an effect, the oil separator, the pump and the like are not installed, so that it is possible to avoid an increase in the size of the body, and it is possible to mount it on a vehicle or the like. In addition to being able to exert the effect, the manufacturing cost can be reduced.

[Brief description of drawings]

FIG. 1 is a vertical cross-sectional view of a scroll compressor according to a first embodiment.

2 is a cross-sectional view taken along the line II-II in FIG. 1 of the scroll compressor according to the first embodiment.

FIG. 3 is an enlarged partial cross-sectional view showing the inner end surface of the housing and the essential parts such as slinger according to the scroll compressor of the first embodiment.

FIG. 4 is an enlarged plan view of a slinger according to the scroll compressor of the first embodiment.

FIG. 5 is an enlarged partial cross-sectional view showing a main part of an inner end surface of a housing and a slinger according to the scroll compressor of the first embodiment.

FIG. 6 is a perspective view of a slinger according to a scroll compressor of a second embodiment.

FIG. 7 is a perspective view of a slinger according to a scroll compressor of a third embodiment.

[Explanation of symbols]

62a ... Suction port 62d ... Communication port 62b
... Suction passage 30 ... Front housing 22 ... Shell portion 38 ... Rear housing 2 ... Fixed scroll 31 ... Shaft sealing device 32 ... Bearing 33 ...
Drive shaft 21 ... Fixed side plate 23 ... Fixed scroll body 4 ... Movable scroll 41 ... Movable side plate 42 ... Movable scroll body 1 ... Compression chamber 1a ... Inner wall side compression chamber 1b ... Outer wall side compression chamber 34 ...
Drive pin 37 ... Radial bearing 36 ... Drive bush 51a, 51, 30a, 41a ... Rotation prevention mechanism (51a
... Rotation prevention pin, 51 ... Movable ring, 30a, 41a ...
Restriction hole) 62c ... Refrigerant passage 30b ... Inner end surface 33b, 61, 62 ... Slinger 61a ... Guide groove 62a ... Guide convex portion

Claims (3)

[Claims] 1. A housing having an intake passage having an intake opening and a communication opening, a bearing mounted in the housing in a low pressure region communicating with the communication opening, and a shaft sealing device for sealing the interior of the housing. Drive shaft supported by the housing through the bearing, a fixed scroll having a fixed side plate and a fixed spiral body and fixed to the housing, and a fixed scroll housed in the housing and meshed with the fixed scroll. A movable side plate and a movable spiral body, and an inner wall side compression chamber communicating with the communication port through the low pressure region is formed on the inner wall side of the movable spiral body, and the communication port is formed on the outer wall side of the movable spiral body. And a movable scroll which forms an outer wall side compression chamber communicating with the low pressure range and a drive bush which engages with a drive pin protruding from the rear end of the drive shaft and revolves the movable scroll via a radial bearing. When A rotation preventing mechanism that engages with the housing and the movable side plate of the movable scroll in the low pressure region to prevent the movable scroll from rotating, and the inner wall side compression chamber and the outer wall are rotated by the orbital motion of the movable scroll. A scroll type compressor in which the side compression chambers are sequentially moved toward the center of the spiral to be hermetically closed, and then the volume is reduced to form a single compression chamber, whereby the refrigerant gas sucked from the suction port is compressed and discharged. In the above, the communication port is opened at a radial position of the fixed scroll body and the movable scroll body, and at least one of the inner wall side compression chamber and the outer wall side compression chamber before being sealed with the shaft sealing device is a refrigerant passage. And an inner end surface orthogonal to the drive shaft is formed in the housing so as to secure a gap communicating with the shaft sealing device, and the drive shaft is synchronously rotated facing the inner end surface. , Scroll compressor, wherein a slinger which allowed to reach the low pressure zone moves the refrigerant gas in the radially outward direction is provided by the viscosity and the centrifugal force of the refrigerant gas to be interposed. 2. The scroll type compressor according to claim 1, wherein the slinger has a guide groove or a guide convex portion formed in the radial direction on the inner end face side. 3. The scroll compressor according to claim 1, wherein the slinger is formed integrally with the drive shaft.