JPH07158566A - Scroll type compressor - Google Patents

Abstract

PURPOSE:To cool and lubricate a shaft sealing device, without generating a large size of the structure and a high manufacturing cost in a compressor, and under a low suction resistance. CONSTITUTION:The communicating hole 62d of a suction passage 62b is opened to the radiating position of a fixed scroll body 23 and a movable scroll body 42. To the holder of a bearing 32, an inclining groove and a vane to guide the refrigerant gas in a low pressure range to a shaft sealing device 31 by the rotation are formed. The shaft sealing device 31 and the outermost outer wall compression chamber prior to the sealing are communicated through a refrigerant passage 62c.

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 orbiting 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 that compresses and discharges the refrigerant gas, the communication port is opened at the radial position of the fixed scroll and the movable scroll, and the bearing is rotated so that the low pressure range Guide means for guiding the medium gas to the shaft sealing device is formed, and the shaft sealing device communicates with at least one of the outermost inner wall side compression chamber and the outer wall side compression chamber before being sealed by a refrigerant passage. Is taking a new step.

(2) In the compressor of the present invention, the guide means is
It can be an inclined groove provided in the cage of the bearing so that the low pressure region side inclines forward in the rotational direction with respect to the axial direction. (3) Further, in the compressor of the present invention, the guide means may be a blade protruding in the low pressure region side and the rear side in the rotation direction of the cage of the bearing. (4) Further, in the compressor of the present invention, it is preferable that the movable ring of the rotation preventing mechanism has a communication hole penetrating the communication port and the bearing.

[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.

Further, the refrigerant gas sucked into the low pressure region from the communication port is guided to the shaft sealing device by the guide means formed in the rotating bearing. Then, the refrigerant gas guided to the shaft sealing device is sucked into at least one of the outermost inner wall side compression chamber and the outer wall side compression chamber before being sealed by the refrigerant passage. The refrigerant gas sucked into one of the outermost inner wall-side compression chamber and the outermost wall-side compression chamber is always in communication with the other because the movable scroll is meshed with the fixed scroll while being out of phase with each other. The refrigerant gas is sucked into the other, and the refrigerant gas is sucked into both the outermost inner wall side compression chamber and the outermost wall side compression chamber.

(2) In the compressor of claim 2, since the inclined groove of the cage in the bearing is recessed so that the low pressure region side inclines forward in the rotational direction with respect to the axial direction, the cage is rotated. For example, the angular velocity causes a parallel component force in the direction of the inclined groove. Due to this parallel component force, the refrigerant gas in the inclined groove is pushed out to the shaft sealing device side. As a result, the low-pressure region side has a lower pressure and the shaft sealing device side has a higher pressure, so that a pumping action from the low-pressure region side to the shaft sealing device occurs, and the refrigerant gas in the low-pressure region is
The rotation of the cage causes it to flow through the inclined groove and is guided by the shaft sealing device.

(3) In the compressor according to the third aspect of the present invention, since the blades of the bearing retainer protrude from the low pressure region side and the rear side in the rotational direction, the blades move to the low pressure region side when the retainer rotates. By scraping the refrigerant gas into the cage, the low-pressure region side has a lower pressure and the shaft-sealing device side has a higher pressure, which causes a pumping action from the low-pressure region side to the shaft-sealing device. Therefore, the refrigerant gas in the low pressure region flows in the axial direction in the cage due to the rotation of the cage and is guided to the shaft sealing device.

(4) When the movable ring of the rotation prevention mechanism is not provided with a communication hole for communicating the communication port and the bearing, the refrigerant gas sucked into the low pressure region from the communication port is of the rotation prevention mechanism. It will reach the guide means of the bearing through the gap. In this regard, in the compressor of claim 4, since the movable ring of the rotation preventing mechanism has the communication hole penetrating the communication port and the bearing, the refrigerant gas in the low pressure region passes through the communication hole,
The bearings are easily supplied. Therefore, the refrigerant gas is more easily guided to the shaft sealing device.

[0016]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments of the compressor according to claims 1 to 4 will be described below with reference to the drawings. This compressor is shown in FIG.
As shown in FIG. 5, a fixed scroll including a fixed side plate 21, a shell portion 22 integrally formed with the fixed side plate 21 and forming an outer shell, and a fixed scroll 23 formed inside the fixed side plate 21 by an involute curve or the like. The compression chamber 1 is formed by meshing with the movable scroll 4 composed of the movable side plate 41 and the movable scroll 42 formed by an involute curve or the like inside the movable side plate 41.

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.
It is fastened to the front housing 30 and the rear housing 38 with the through bolt 3 (see FIG. 2). A drive shaft 33 extends in the boss of the front housing 30 via a shaft sealing device 31, and a large diameter portion 33a is formed behind the drive shaft 33, and the front housing 30 and the large diameter portion 33a are formed. Angular contact ball bearing 32 between
Is intervening.

As shown in FIGS. 3 to 5, the bearing 32 includes an outer ring 32a, an inner ring 32b, and the outer ring 32a and the inner ring 3.
2b, and a cylindrical retainer 32d that holds a ball 32c as a rolling element. On the outer peripheral surface of the retainer 32d, as the most characteristic configuration of this compressor, an inclined groove 32e is provided which inclines forward in the rotational direction on the low pressure region side, which will be described later, with respect to the axial direction. A blade 32f is provided so as to project on the region side and the rear side in the rotation direction. The holder 32d is a resin molded product. The inclined groove 32e and the blade 32f are guide means. And
Outermost outer wall side compression chamber 1b before being sealed with the shaft sealing device 31
As a characteristic configuration of this compressor, as shown in FIG. 1, they are communicated with each other by a refrigerant passage 62c.

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. Movable ring 5
1 has a communication port 62 as a characteristic configuration of this compressor.
A communication hole 51b that allows the d and the bearing 32 to communicate with each other is provided therethrough. 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 rotation prevention pin 51
The front and rear surfaces of the movable ring 51 not provided with a are slidably in contact with the front housing 30 and the movable side plate 41, whereby the thrust force acting from the movable side plate 41 is received. 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.

The refrigerant gas sucked into the low pressure region through the communication port 62d is guided to the shaft sealing device 31 by the guide means formed in the rotating bearing 32. That is, the bearing 32
When the retainer 32d rotates, the force F is generated in the rotation direction in the inclined groove 32e due to the angular velocity ω, as shown in FIG. This force F is a vertical component force F in the vertical direction of the inclined groove 32e.
n and a parallel component force Fs in the direction of the inclined groove 32e. The parallel component force Fs pushes the refrigerant gas in the inclined groove 32e toward the shaft sealing device 31 side. At this time, blade 3
2f scrapes the refrigerant gas on the low pressure side into the inclined groove 32e. As a result, the low-pressure region side has a lower pressure P ₀ and the shaft sealing device 31 side has a higher pressure P ₁ (P ₁ > P ₀ ), so that a pumping action from the low pressure region side to the shaft sealing device 31 occurs. Therefore, the refrigerant gas in the low pressure region flows in the inclined groove 32e in the axial direction at the flow rate Q by the rotation of the retainer 32d, and the shaft sealing device 31
Will be guided to. During this time, the movable ring 51 of the rotation prevention mechanism
Is a communication hole 51 for communicating the communication port 62d with the bearing 32.
Since b is penetrated, the low-pressure region refrigerant gas is easily supplied to the bearing 32 through the communication hole 51b. Therefore, the refrigerant gas is guided to the shaft sealing device 31 more easily.

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.
This flow is shown by an arrow in FIG. After that, the refrigerant passage 62
By c, it is sucked into the outermost outer wall side compression chamber 1b before being sealed. Further, a part of the refrigerant gas lubricates the bearing 32, the radial bearing 37, the rotation preventing mechanism and the like, and is sucked into the outermost inner wall side compression chamber 1a and the outer wall side compression chamber 1b before being sealed.

The refrigerant gas sucked into the outermost compression chamber 1b on the outer wall side is meshed with the fixed scroll 2 while the movable scroll 4 is out of phase with each other, whereby the compression chamber 1b on the outer wall side is compressed into the compression chamber on the inner wall side. Since it is always communicated with 1a, the refrigerant gas is sucked into the inner wall side compression chamber 1a, and the refrigerant gas is sucked into both the outermost inner wall side compression chamber 1a and the outer wall side compression chamber 1b. In this way, the inner wall side compression chamber 1a and the outer wall side compression chamber 1b are sequentially moved toward the center of the spiral from the outermost side and sealed, and then the volume is reduced to form a single compression chamber 1c. The sucked refrigerant gas is discharged into the discharge chamber 39 through the discharge port 2 and the discharge valve mechanism 3, and is circulated from the discharge port to the external refrigeration circuit.

Therefore, in this compressor, the shaft sealing device 3
Since the refrigerant gas can be easily supplied to 1, the shaft seal 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, etc., high compression efficiency can be maintained.

Further, in this compressor, in order to exert such an effect, the conventional oil separator, pump, etc. are not installed, so that it is possible to avoid an increase in size and it is excellent for vehicles and the like. It is possible to realize excellent mountability and to reduce the manufacturing cost. Further, in this compressor, since the lubricating oil in the compressed refrigerant gas is not supplied to the shaft sealing device 31, the refrigerant gas is not re-expanded and re-compressed, and high compression efficiency can be maintained. it can.

In addition, in this compressor, the suction passage 62b
The passage area of the suction passage 62 is not reduced.
The suction resistance does not increase due to b, and high compression efficiency can be secured. Further, in this compressor, since the retainer 32d is a resin molded product, it can be manufactured at low cost. Even if the retainer 32d is a pressed metal product, the manufacturing cost is not so much increased by changing the press die.

Although the inclined groove 32e is provided on the outer peripheral surface of the retainer 32d in the above embodiment, similar inclined grooves and blades are formed on the inner peripheral surface of the retainer 32d and the region of the inner ring 32b where the balls 32c do not roll. It is also effective to form.

[0031]

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, etc. are not installed, so that it is possible to avoid an increase in the size of the physique, and it is possible to mount the compressor excellently 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 an embodiment.

FIG. 2 relates to a scroll compressor according to an embodiment, and I of FIG.
It is a sectional view taken along the line I-II.

FIG. 3 is a partial cross-sectional perspective view of a bearing according to the scroll compressor of the embodiment.

FIG. 4 is a plan view of a bearing according to the scroll compressor of the embodiment.

FIG. 5 is a partial cross-sectional side view of a bearing according to the scroll compressor of the embodiment.

FIG. 6 is an explanatory diagram related to the scroll compressor of the embodiment and showing the flow of the refrigerant gas while the cage of the bearing is rotating.

[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 32e, 32f ... Guide means (32e ... Inclined groove, 32f ...
Vane) 62c ... Refrigerant passage 51b ... Communication hole

Claims (4)

[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 and the movable scroll, and the bearing is formed with guide means for guiding the refrigerant gas in the low pressure region to the shaft sealing device by rotation. At least one of the inner wall side compression chamber and the outermost wall compression chamber before being sealed with the shaft sealing device is communicated with a refrigerant passage. 2. The scroll-type compression device according to claim 1, wherein the guide means is an inclined groove formed in the retainer of the bearing so that the low pressure region side inclines forward in the rotational direction with respect to the axial direction. Machine. 3. The scroll type compressor according to claim 1, wherein the guide means is a blade protruding in the low pressure region side and the rear side in the rotation direction of the cage of the bearing. 4. The scroll compressor according to claim 1, wherein the movable ring of the rotation preventing mechanism has a communication hole penetrating the communication port and the bearing.