JP2003214339A - Opened type compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To prevent a clutch from slippage by attaching of oil contained in leaked gas on a friction surface of the clutch. <P>SOLUTION: A through hole 15 is made into a communicating passage 14 by providing the through hole 15 communicated between a space 23 formed on the outside of a sealing member 20 and the outside of a housing 2 on a crankshaft 10 to make a revolving scroll 41 take normal revolving motion. Refrigerant gas is discharged outside of the housing 2 through the communicating passage 14 communicated to the space 23 in the case when the refrigerant gas is the housing 2 and misty refrigerator oil contained in the refrigerant gas is leaked in the inside of the space 23 on the outside of the sealing member 20. Slippage is never caused on the clutch 25 as the leaked gas works on the clutch 25 and the oil contained in the refrigerant gas is attached on the friction surface of the clutch 25, and it becomes possible to transmit motive power from a driving source to the side of the crankshaft 10 without loss. <P>COPYRIGHT: (C)2003,JPO

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a compressor, and more particularly to an open type compressor.

[0002]

2. Description of the Related Art A scroll type compressor is shown in FIG. 9 as an example of this type of compressor. In this scroll type compressor 55, a cup-shaped first housing 56A and a funnel-shaped second housing 56B are fastened together with bolts or the like to form a housing 56 that serves as an airtight container. Here, the first housing 56A, the fixed scroll 57 provided in the housing 56, the orbiting scroll 58 which is provided in the housing 56A so as to be rotatable, and which meshes with and engages with the fixed scroll 57, and the second A crankshaft 61, which is rotatably provided in the housing 56B via a main bearing 59 and an auxiliary bearing 60, and is connected to the orbiting scroll 58, a crankshaft 61, and the housing 56B.
A seal member 62 for sealing between the crankshaft 61 and
A drive source (not shown) for rotationally driving the clutch, and a clutch 6 for transmitting or disconnecting the drive force of the drive source to the crankshaft 61.
3 and 3.

Then, the drive source is driven to drive the clutch 63.
When the crankshaft 61 is rotated by transmitting the driving force of the drive source to the crankshaft 61, the orbiting scroll 58 follows the rotation of the crankshaft 61 and makes an orbiting movement with respect to the fixed scroll 57. Accordingly, the low-temperature low-pressure refrigerant gas is sucked into the housing 56 through the suction port (not shown).

Here, part of the refrigerant gas is the housing 5
6 is guided to the seal member 62 side through the gap between the components of the main bearing 59, and the atomized oil component contained in the refrigerant gas is supplied to the sliding portion of the seal member 62, and the sliding portion The space between the crankshaft 61 and the crankshaft 61 is lubricated.

On the other hand, most of the other refrigerant gas sucked into the housing 56 is introduced between the fixed scroll 57 and the orbiting scroll 58, and compressed between them to become a high temperature and high pressure refrigerant gas and then discharged. It will be discharged from the outlet (not shown) to the outside of the housing 56.

[0006]

However, in the scroll type compressor 55 having the above-described structure, the refrigerant gas acting on the seal member 62 or the atomized refrigerating machine oil contained in the refrigerant gas is caused by some reason. When leaking to the outside of the seal member 62, the pressure in the space 64 between the seal member 62 and the auxiliary bearing 60 located outside the seal member 62 increases, and the refrigerant gas flows from this space 64 to the components of the auxiliary bearing 60. By leaking to the outside through the gap, the lubricating oil sealed inside the sub bearing 60 leaks to the clutch 63 side. In this case, since the lubricating oil of the sub bearing 60 is exhausted, the sub bearing 6
There was a problem that the life of 0 decreased. Further, the atomized refrigerating machine oil contained in the leaking refrigerant gas and the oil component inside the auxiliary bearing 60 adhere to the friction surface of the clutch 63. Therefore, when the clutch 63 is engaged, slippage occurs in the clutch 63, abnormal noise is generated, or power from the drive source cannot be sufficiently transmitted to the crankshaft 61, and the refrigerant gas is compressed. There was a problem that the performance would drop significantly.

As a conventional technique for solving this problem, for example, it is known to provide a lateral hole 70 in the cylindrical portion of the second housing 56B shown in FIG.
For some reason, refrigerant gas or refrigerating machine oil from the seal member 6
In the case of leakage to the outside of 2, the refrigerant gas and the refrigerating machine oil are released from the lateral holes to the atmosphere, so that the pressure in the space 64 between the seal member 62 and the auxiliary bearing 60 located outside thereof is increased. Prevent and solve the above problems. However, in this conventional technique, since the lateral hole 70 is opened in the radial direction of the second housing 56B while avoiding the bearing 71, it is inevitable that the total length of the compressor becomes large, which is one of the factors that hinder the miniaturization. Was becoming.

The present invention has been made in view of the above conventional problems, and the lubricating oil inside the sub bearing leaks to the clutch side due to the refrigerant gas and the refrigerating machine oil leaking to the outside of the seal member, and Prevents damage, and also prevents refrigerating machine oil and auxiliary bearing lubricating oil from acting on the friction surface of the clutch,
Accordingly, it is an object of the present invention to provide a compressor that can sufficiently transmit power from a drive source to the crankshaft side, obtain desired compression performance, and prevent an increase in overall length.

[0009]

The present invention employs the following means in order to solve the above problems. That is, the invention according to claim 1 is a compressor which forms an outline of a compressor by hermetically connecting a first housing and a second housing, and a working fluid is compressed in the first housing. A compression mechanism is installed, and a main bearing and a sub-bearing are installed in order from the joint surface side with the first housing in the inner diameter tubular portion of the second housing, and fixedly supported on the main bearing and the sub-bearing. A crankshaft, one end of which is connected to the compression mechanism and the other end of which is configured to transmit or cut off power from a drive source that rotationally drives the crankshaft to or from the crankshaft. The crankshaft is a compressor in which the inside and the outside of the compressor are sealed by a ring-shaped seal member installed between the main bearing and the sub bearing of the inner diameter cylindrical portion of the second housing. Yes, the above The communicating passage for communicating the space and the second housing external composed seal member and the sub-bearing and the inside diameter tubular portion of the second housing, characterized in that provided on the crankshaft. According to the compressor of the present invention, the refrigerant gas leaked from the inside of the housing to the portion outside the seal member and the atomized refrigerating machine oil contained in the refrigerant gas are discharged to the outside of the housing through the communication passage provided in the crankshaft. Will be done.

According to a second aspect of the present invention, in the compressor according to the first aspect, the leakage gas discharge passage communicates between a portion outside the seal member and the outside of the housing. It is characterized by comprising a through hole provided in the crankshaft. According to the compressor of the present invention, the refrigerant gas and the refrigerating machine oil leaking from the inside of the housing to the portion outside the seal member are discharged to the outside of the housing through the communication passage formed by the through hole provided in the crankshaft. Become.

The invention according to claim 3 is the compressor according to claim 1, wherein a space formed by the seal member, the auxiliary bearing, and an inner diameter cylindrical portion of the second housing, and an outer portion of the second housing. The communication passage that communicates with and includes a cutout portion provided in the outer diameter portion of the crankshaft. According to the compressor of the present invention, the refrigerant gas and the refrigerating machine oil leaking from the inside of the housing to the portion outside the seal member are discharged to the outside of the housing through the communication passage formed by the notch provided in the crankshaft. Become.

According to a fourth aspect of the present invention, there is provided a compressor which forms an outline of the compressor by hermetically connecting the first housing and the second housing, and the first housing is provided with a working fluid. A compression mechanism for compressing is installed, and a main bearing and a sub-bearing are installed in the inner diameter tubular portion of the second housing in order from the joint surface side with the first housing, and fixed to the main bearing and the sub-bearing. A clutch that has a supported crankshaft, one end of which is connected to the compression mechanism, and the other end of which transmits or cuts off power from a drive source that rotationally drives the crankshaft to the crankshaft. A compressor in which the crankshaft is sealed between the inside and the outside of the compressor by a ring-shaped seal member installed between the main bearing and the sub bearing of the inner diameter tubular portion of the second housing. And before A communication passage that connects the space formed by the seal member, the auxiliary bearing, and the inner diameter cylindrical portion of the second housing with the outside of the end surface of the second housing is provided in the inner diameter cylindrical portion of the second housing. And According to the compressor of the present invention, the refrigerant gas and the refrigerating machine oil leaking from the inside of the housing to the outside of the seal member are discharged to the outside of the housing through the communication passage provided in the inner diameter cylindrical portion of the second housing. It will be.

According to a fifth aspect of the present invention, in the compressor according to the fourth aspect, a space formed by the seal member, the auxiliary bearing, and an inner diameter cylindrical portion of the second housing, and an outer portion of the second housing. The communication passage communicating with and is composed of a groove or a through hole provided in the inner diameter cylindrical portion of the second housing. According to the compressor of the present invention, the refrigerant gas and the refrigerating machine oil leaking from the inside of the housing to the outside of the seal member are passed through the communication passage formed of the groove or the through hole provided in the inner diameter tubular portion of the second housing. It will be discharged to the outside of the housing.

The invention according to claim 6 is the compressor according to claim 5, wherein the second housing is a cast product made of a material such as an aluminum alloy or cast iron. The groove provided in the inner diameter tubular portion is formed by casting. According to the compressor of the present invention,
When molding the second housing by casting, a groove is simultaneously formed in the cylindrical portion of the inner diameter of the second housing.

According to a seventh aspect of the present invention, there is provided a compressor which forms an outer shell of the compressor by hermetically connecting the first housing and the second housing, and the working fluid is supplied to the first housing. A compression mechanism for compressing is installed, and a main bearing and a sub-bearing are installed in the inner diameter tubular portion of the second housing in order from the joint surface side with the first housing, and fixed to the main bearing and the sub-bearing. A clutch that has a supported crankshaft, one end of which is connected to the compression mechanism, and the other end of which transmits or cuts off power from a drive source that rotationally drives the crankshaft to the crankshaft. A compressor in which the crankshaft is sealed between the inside and the outside of the compressor by a ring-shaped seal member installed between the main bearing and the sub bearing of the inner diameter tubular portion of the second housing. And before A communication passage that connects a space formed by the seal member, the auxiliary bearing, and the inner diameter cylindrical portion of the second housing with the outer circumference of the inner diameter cylindrical portion of the second housing is provided in the inner diameter cylindrical portion of the second housing. Is characterized by. According to the compressor of the present invention, the refrigerant gas leaked from the inside of the housing to the portion outside the seal member and the atomized refrigerating machine oil contained in the refrigerant gas pass through the communication passage provided in the inner diameter tubular portion of the second housing. It will be discharged to the outside of the housing through.

The invention according to claim 8 is the compressor according to claim 7, wherein the space formed by the seal member, the auxiliary bearing, and the inner diameter tubular portion of the second housing, and the second housing. The communication passage that communicates with the outer circumference of the inner diameter tubular portion comprises a groove provided on the outer peripheral surface of the inner diameter tubular portion of the second housing and a through hole that communicates with the groove from the inner peripheral surface of the inner diameter tubular portion. And According to the compressor of the present invention, the refrigerant gas and the refrigerating machine oil leaked from the inside of the housing to the outside of the seal member are provided with the groove provided on the outer peripheral surface of the inner diameter cylinder of the second housing and the inner peripheral surface of the inner diameter cylinder. Is discharged to the outside of the housing through the through hole communicating with this groove.

The invention according to claim 9 is the compressor according to claim 8, wherein the second housing is a cast product made of a material such as an aluminum alloy or cast iron. The groove provided on the outer peripheral surface of the inner diameter tubular portion is characterized by being molded by casting. According to the compressor of the present invention, when the second housing is molded by casting, the groove is simultaneously formed in the inner diameter tubular portion of the second housing.

According to a tenth aspect of the present invention, in the compressor according to the eighth aspect, the groove provided on the outer peripheral surface of the inner diameter cylindrical portion of the second housing has a part of the outer peripheral surface of the cylinder having an oval cross section. It is characterized by being molded into. According to the compressor of the present invention, a groove is formed between the outer peripheral surface of the cylinder and the component mounted on the outer peripheral surface of the inner diameter cylindrical portion by forming a part of the outer peripheral surface of the cylinder into the shape of an open circular section.

[0019]

BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of the present invention shown in the drawings will be described below. 1 and 2 show a first embodiment of a scroll type compressor as an example of an open type compressor according to the present invention. The scroll type compressor 1 is a horizontal type scroll type compressor. A compressor, which is a housing 2, a fixed scroll 31, and an orbiting scroll 4.
1, a crankshaft 10, and a clutch 25.

The housing 2 is composed of a cup-shaped housing body (first housing) 3 and a lid member (second housing) 4 that closes an opening of the housing body 3, and an inner space of the housing body 3 is formed. A fixed scroll 31 and an orbiting scroll 41 are provided inside, and the crankshaft 10 is rotatably mounted at the center of the lid member 4. The housing body 3 is provided with a suction port (not shown) for introducing the refrigerant gas into the inner space and a discharge port (not shown) for discharging the refrigerant gas from the inner space.

The lid member 4 includes a substantially tubular main body portion 5 and a boss 6 which is integrally provided at one axial end of the main body portion 5 and which constitutes a substantially tubular inner diameter tubular portion having a smaller diameter than the main body portion 5. And a flange portion 7 having a flange shape integrally provided between the main body portion 5 and the boss 6. In the state where the main body portion 5 is fitted to the inner peripheral side of the opening end portion of the housing main body 3, the flange portion 7 is formed. Is fastened to the opening end surface of the housing body 3 with a bolt so that the housing body 3 can be mounted on the housing body 3 side.

An inner bearing (main bearing) 8 is mounted on the inner peripheral side of the main body 5 of the lid member 4, and a crank arm 12 of a crankshaft 10 described later is fitted inside the inner bearing 8. Has become. An outer bearing (sub-bearing) 9 is mounted on the inner peripheral side of the boss 6 of the lid member 4, and a main shaft 11 of a crankshaft 10 described later is fitted inside the outer bearing 9.

The crankshaft 10 is a rod-shaped main shaft 11
And a disk-shaped crank arm 12 integrally provided on one end of the main shaft 11 in a state where the axes are aligned with each other, and an axis of the main shaft 11 is integrally provided on one side surface of the crank arm 12 with the axis decentered. It is composed of a rod-shaped crank pin 13, and a clutch 25 is attached between the other end of the main shaft 11 and the boss 6 of the lid member 4.

The main shaft 11 of the crankshaft 10 is rotatably supported by the outer bearing 9 mounted on the inner peripheral side of the boss 6 of the lid member 4, and the crank arm 12 is the inner peripheral surface of the main body portion 5 of the lid member 4. It is rotatably supported by an inner bearing 8 mounted on the side. The seal member 20 is provided between the inner peripheral surface of the boss 6 of the lid member 4 and the peripheral surface of the crankshaft 10.
Is attached, and the seal member 20 causes the space between them 6 and 1
0 is to be sealed. The crank pin 13 of the crank shaft 10 is fitted inside a bush 50 described later. A balance weight 40 is provided on the end surface of the crank arm 12 of the crankshaft 10 to cancel an unbalance amount given to a revolving scroll 41 described later.

At the center of the main shaft 11 of the crankshaft 10,
A through hole 15 is provided, one end of which opens into the other end surface of the main shaft 11 and the other end of which opens into a space 23 formed between a seal member 20 and an outer bearing 9 which will be described later. It serves as a leakage gas discharge passage (communication passage) 14 that communicates between 23 and the outside of the housing 2.

The seal member 20 includes an annular main body portion 21 fitted to the inner peripheral side of the boss 6 of the lid member 4, and the main body portion 21.
Of the main shaft 11 of the crankshaft 10 by slidingly contacting the peripheral surface of the main shaft 11 of the crankshaft 10 to seal the main shaft 11. ing. The seal member 20 is made of rubber-like elastic material, synthetic resin, or the like. Sealing member 20
A cylindrical space 23 is formed between the outer side and the outer bearing 9, and the other end of the leakage gas discharge passage 14 is opened in the space 23.

The clutch 25 is attached to the rotor 26 rotatably on the outer peripheral side of the boss 6 of the lid member 4 via a bearing 24, and is integrally attached to the other end of the main shaft 11 of the crankshaft 10 and also to the rotor 26. A clutch plate 29 provided facing one side surface of the rotor 26 and displaceable in the direction of the rotor 26, and provided in a groove 28 provided on the other side surface of the rotor 26 and fixed to the lid member 4 side. And a coil 30.

In this case, a groove 27 for the V-belt is provided on the outer peripheral surface of the rotor 26, and a drive source (not shown) is provided through the V-belt (not shown) hooked on the groove 27 for the V-belt. No)).

By energizing the coil 30, a magnetic circuit is formed between the rotor 26 and the clutch plate 29, the clutch plate 29 is attracted to the rotor 26, and the driving force of the driving source is the V belt and the rotor 26. , And clutch plate 2
9 is transmitted to the crankshaft 10 and the crankshaft 10
Is driven to rotate.

The fixed scroll 31 is a disk-shaped substrate 32.
And a spiral fixed-side wrap 33 that is integrally erected on one end surface of the substrate 32. With the fixed-side wrap 33 facing the lid member 4, the substrate 32 is fixed to the housing main body 3. It is configured to be fixed to the housing body 3 by being fastened to the bottom portion with bolts.

An O-ring 37 is interposed between the outer peripheral surface of the base plate 32 of the fixed scroll 31 and the inner peripheral surface of the housing body 3, and the O-ring 37 seals the spaces 32 and 3 between the two to seal the base plate 32. A suction chamber 38 is formed in the left side portion, and a discharge cavity 39 is formed in the right side portion. The suction chamber 38 communicates with a refrigerant gas suction port (not shown) provided in the housing body 3, and the discharge cavity 39 communicates with a discharge port (not shown) provided in the housing body 3. There is.

A discharge port 34 is provided at the center of the substrate 32 of the fixed scroll 31 so as to penetrate the substrate 32 in the axial direction. The discharge port 34 is opened and closed by a discharge valve 35 provided on the discharge cavity 39 side. It has become. The opening / closing angle of the discharge valve 35 is limited by a stopper 36 provided outside the discharge valve 35.

The orbiting scroll 41 includes a disc-shaped substrate 42.
And a swirl-side swirl-side wrap 43 that is integrally provided upright on one end surface of the substrate 42.
Are formed in substantially the same shape as the fixed side wrap 33 of the fixed scroll 31.

The orbiting scroll 41 is a fixed scroll 3
The housing 1 is provided in the housing 2 so as to face the housing 1. Orbiting side wrap 43 of the orbiting scroll 41
And the fixed side wrap 33 of the fixed scroll 31 are eccentric to each other by the orbiting radius, and the side surface of the orbiting side wrap 43 and the side surface of the fixed side wrap 33 are in line contact with each other at a plurality of points. It is adapted to be engaged with each other with a phase of 180 °.

Tip seals 45 and 44 are attached to the tip end surface of the swivel side wrap 43 and the tip end surface of the fixed side wrap 33, respectively, and the tip seals 45 and 44 mesh the fixed side wrap 33 and the swivel side wrap 43, respectively. When they are engaged with each other, they are brought into close contact with the mating base plates 42 and 32, respectively, so that the fixed side wrap 33 and the swiveling side wrap 43 are compressed spaces which are substantially symmetrical with respect to their centers. Room 4
6 is formed.

A cylindrical boss 48 is integrally provided in the central portion of the other end surface of the base plate 42 of the orbiting scroll 41 in a state of protruding in the axial direction, and an orbiting bearing 49 is provided inside the boss 48. The bush 50 is rotatably mounted, and the crank pin 13 of the crankshaft 10 is fitted inside the bush 50.

A rotation blocking portion 51 is provided on the outer peripheral side of the boss 48 of the orbiting scroll 41. The rotation blocking portion 51 allows the revolving orbiting operation of the orbiting scroll 41.
It is designed to prevent its rotation.

When the drive source is driven and the clutch 25 is actuated to attract the clutch plate 29 to the rotor 26 side, the drive force of the drive source is V belt and the rotor 2 side.
It is transmitted to the crankshaft 10 via 6 and the clutch plate 29, and the crankshaft 10 is rotationally driven. Crankshaft 10
When the orbit is rotated, the rotation is transmitted to the orbiting scroll 41 via the crank pin 13, the bush 50, the orbiting bearing 49, and the boss 48, and the orbiting scroll 41 is rotated by the rotation preventing portion 5.
In the state in which the rotation is blocked by 1, the orbiting motion of the fixed scroll 31 is carried out on the circular orbit centered on the main shaft 11 of the crank shaft 10 and having the eccentric amount of the crank pin 13 as its radius. In this case, low-temperature, low-pressure refrigerant gas is sucked into the housing 2 through the suction port as the orbiting scroll 41 orbits, and the fixed-side wrap 33 of the fixed scroll 31 and the orbiting-side wrap of the orbiting scroll 41 are charged with the refrigerant gas. 43
Is compressed in the compression chamber 46 between them and becomes high-temperature, high-pressure refrigerant gas, which is guided from the discharge port 34 into the discharge cavity 39 through the discharge valve 35 and from the discharge cavity 39 to a discharge port (not shown). Will be discharged to the outside of the housing 2 via.

In the above process, a part of the refrigerant gas sucked into the suction chamber 38 through the suction port is partially sucked into the suction chamber 3.
8 acts on the seal member 20 through the gap between the components of the inner bearing 8 and the sliding portion 22 of the seal member 20 is lubricated by the atomized refrigerating machine oil contained in the refrigerant gas.

Here, when the refrigerant gas or the refrigerating machine oil acting on the sliding portion 22 of the seal member 20 leaks into the space 23 outside the sealing member 20 through the sliding portion 22 of the seal member 20 for some reason. Since the space 23 is open to the atmosphere by the leak gas discharge passage 14 formed of the through hole 15 provided in the main shaft 11 of the crankshaft 10, the leak gas is discharged to the outside of the housing 2 through the leak gas discharge passage 14. Will be discharged.

Therefore, the space 23 outside the sealing member 20
Since the internal pressure does not increase due to the leaked gas, the refrigerant gas and the refrigerating machine oil do not leak to the outside through the gaps between the components of the outer bearing 9, and the lubrication sealed inside the outer bearing 9 does not occur. Oil does not leak outside. For this reason, the friction oil of the refrigerating machine oil and the inside of the outer bearing 9 does not adhere to the friction surface of the clutch plate 29, and the clutch plate 29 does not slip. As a result, the driving force from the driving source can be reliably transmitted to the crankshaft 10 side via the clutch 25, so that a desired compression performance can be obtained. Further, since the lubricating oil of the outer bearing 9 is not exhausted, the outer bearing 9 can be prevented from being damaged. Further, according to this configuration, the through hole 1 is formed in the crankshaft 10 without providing a radial hole in the boss 6 of the lid member 4.
Since No. 5 is provided, it is possible to prevent the entire length of the compressor from being increased and to reduce the size of the compressor in spite of providing the hole for discharging the leaked gas.

FIG. 3 shows a second embodiment of the scroll compressor according to the present invention. This scroll compressor 1 has a crankshaft 10 corresponding to an inner peripheral surface of an outer bearing 9. A cutout portion 16 extending in the axial direction is provided in the main shaft 11.
Is provided, and the notch 16 communicates the space 23 outside the seal member 20 and the outside of the housing 2 with the leakage gas discharge passage 14
Other configurations are the same as those shown in the first embodiment.

In addition, even in the case shown in this embodiment, the same operational effects as those shown in the first embodiment can be obtained, and the refrigerant gas acting on the sliding portion 22 of the seal member 20 and the refrigeration Due to machine oil for some reason, the seal member 20
The space 23 outside the seal member 20 through the sliding portion 22 of
Even if it leaks into the interior, the leaked gas is notched 1
Since the gas is discharged to the outside of the housing 2 by the leak gas discharge passage 14 composed of 6, the pressure in the space 23 is increased by the leak gas, and the refrigerant gas and the refrigerating machine oil are kept in the outer bearing 9
There is no leakage to the outside through the gap between the parts, and the lubricating oil sealed inside the outer bearing 9 also does not leak to the outside. Therefore, these oil components are
It will not act on. Therefore, the driving force from the driving source can be reliably transmitted to the crankshaft 10 side via the clutch 25, and desired compression performance can be obtained. Further, since the lubricating oil of the outer bearing 9 is not exhausted, the outer bearing 9 can be prevented from being damaged. further,
In this configuration, since the notch 16 is provided as a hole for discharging the leaked gas in the crankshaft 10, it is possible to prevent an increase in the total length of the compressor.

FIG. 4 shows a third embodiment of the scroll compressor according to the present invention. This scroll compressor 1 has an inner peripheral surface of a housing 2 corresponding to an outer peripheral surface of an outer bearing 9. A groove 17 extending in the axial direction is provided in the surface portion,
The groove 17 is used as the leak gas discharge passage 14 that communicates the space 23 outside the seal member 20 with the outside of the housing 2, and the other configurations are the same as those shown in the first embodiment. .

In addition, even in the case of this embodiment, the same effect as that of the first embodiment can be obtained, and the refrigerant gas acting on the sliding portion 22 of the seal member 20 and the refrigeration can be frozen. Due to machine oil for some reason, the seal member 20
The space 23 outside the seal member 20 through the sliding portion 22 of
Even if the gas leaks into the inside, the leaked gas is discharged to the outside of the housing 2 through the leaked gas discharge passage 14 including the groove 17, so that the pressure in the space 23 is increased by the leaked gas, and the refrigerant gas and the refrigerating machine oil are discharged. There is no leakage to the outside through the gap between the components of the outer bearing 9, and the lubricating oil sealed inside the outer bearing 9 does not leak to the outside. Therefore, these oils do not act on the clutch 25. Therefore, the driving force from the driving source can be reliably transmitted to the crankshaft 10 side via the clutch 25, and desired compression performance can be obtained. Further, since the lubricating oil of the outer bearing 9 is not exhausted, the outer bearing 9 can be prevented from being damaged. Further, in this configuration, since the groove 17 is provided in the boss 6 as a hole for discharging the leaked gas, it is possible to prevent an increase in the total length of the scroll compressor 1. Further, when the lid member 4 is molded by casting, the boss 6 of the lid member 4 is formed at the same time as the molding of the lid member 4 without separately performing the step of forming the hole for discharging the leaked gas. Since the groove 17 can be formed, the number of manufacturing steps of the scroll compressor 1 can be reduced.

FIG. 5 shows a fourth embodiment of the scroll compressor according to the present invention. This scroll compressor 1 has an inner peripheral edge portion of the housing 2 corresponding to the outer bearing 9, A through hole 18 penetrating between the end surface of the housing 2 and the outer space 23 of the outer bearing 9 is provided.
8 is a leak gas discharge passage 14 that communicates the space 23 outside the outer bearing 9 with the outside of the housing 2, and the other configurations are the same as those shown in the first embodiment.

In addition, even in the case shown in this embodiment, the same effect as that shown in the first embodiment can be obtained, and the refrigerant gas acting on the sliding portion 23 of the seal member 20 and the refrigeration Due to machine oil for some reason, the seal member 20
The space 23 outside the seal member 20 through the sliding portion 23 of
Even if the gas leaks into the inside, the leaked gas is discharged to the outside of the housing 2 through the leaked gas discharge passage 14 including the through hole 18, so that the pressure in the space 23 is increased by the leaked gas, and the refrigerant gas and the refrigerating machine oil are discharged. Does not leak to the outside through the gap between the components of the outer bearing 9 and the outer bearing 9
Lubricating oil enclosed in the inside of the container does not leak outside. Therefore, these oils do not act on the clutch 25. Therefore, the driving force from the driving source can be reliably transmitted to the crankshaft 10 side via the clutch 25, and desired compression performance can be obtained. Further, since the lubricating oil of the outer bearing 9 is not exhausted, the outer bearing 9 can be prevented from being damaged. Furthermore, in this structure, since the through hole 18 is provided in the boss 6 as a hole for discharging the leaked gas, it is possible to prevent an increase in the total length of the compressor.

FIG. 6 and FIG. 7 show a fifth embodiment of the scroll compressor according to the present invention. The scroll compressor 1 includes a housing 2 corresponding to an inner peripheral surface of a bearing 24. Axially extending groove 1 provided on the outer peripheral surface of the
9a and a through hole 19b which communicates the space 23 outside the seal member 20 with the outside of the housing 2 from the groove 19a, the leakage gas discharge passage 14 is formed, and other configurations are the same as those of the first embodiment. Is the same as that shown in FIG.

Also, in the one shown in this embodiment, the same operational effect as that shown in the first embodiment is obtained, and the refrigerant gas acting on the sliding portion 22 of the seal member 20 and the refrigeration are frozen. Due to machine oil for some reason, the seal member 20
The space 23 outside the seal member 20 through the sliding portion 22 of
Even if it leaks into the inside, the leaked gas still leaks through the through hole 19b and the groove 1.
The housing 2 is provided with the leakage gas discharge passage 14 composed of 9a
Since it is discharged to the outside, the pressure in the space 23 is increased by the leaked gas, and the refrigerant gas and the refrigerating machine oil do not leak to the outside through the gaps between the components of the outer bearing 9 and the outer bearing 9 Lubricating oil enclosed in the inside of the container does not leak outside. Therefore, these oils do not act on the clutch 25. Therefore, the driving force from the driving source can be reliably transmitted to the crankshaft 10 side via the clutch 25, and desired compression performance can be obtained.

Further, since the lubricating oil of the outer bearing 9 is not exhausted, the outer bearing 9 can be prevented from being damaged. further,
In this configuration, the groove 19a serves as a communication passage for discharging the leaked gas.
Since the boss 6 and the through hole 19b are provided, it is possible to prevent an increase in the total length of the scroll compressor 1. Further, when the lid member 4 is molded by casting, the communication passage 1 for discharging the leaked gas is formed.
The groove 19a can be formed in the boss 6 of the lid member 4 at the same time as the molding of the lid member 4 without independently performing the step of forming the groove 19a to be the four. The number of manufacturing steps can be reduced.

Alternatively, in order to provide the above-described groove 19a, a part of the outer peripheral surface of the cylinder of the boss 6 is cut into a flat surface so that it is formed into a cut-out circular cross-sectional shape as in the modification shown in FIG. Good. With this configuration, the space of the cutout portion formed between the inner peripheral surface of the bearing 24 and the groove 19a 'serves as the groove 19a', which is advantageous in that it can be easily processed.

The above-described embodiments are all applied to a scroll type compressor, but the present invention is not limited to this, and is applicable to other types of compressors such as a rotary type and a swash plate type. Of course, the same can be applied to.

[0053]

As described above, according to the present invention, the communication passage is provided in the crankshaft and the inner diameter cylindrical portion of the second housing, so that the leakage from the inside of the housing to the outside of the seal member occurs. Refrigerant gas and refrigerating machine oil are discharged to the outside of the housing through the communication passage. Therefore, the refrigerant gas leaked to the outside of the seal member and the oil component contained in the refrigerating machine oil do not act on the clutch through the gap between the components of the auxiliary bearing and do not hinder the operation of the clutch. Power can be reliably transmitted to the crankshaft side via the clutch, and desired compression performance can be obtained. Further, since the refrigerant gas does not pass through the gap of the sub bearing, the lubricating oil of the sub bearing does not run out, and therefore the sub bearing can be prevented from being damaged. Further, since the communication passage is provided in the crankshaft as a hole for discharging the leaked gas, it is possible to prevent an increase in the total length of the compressor.

The same effect can be obtained when the communication passage provided in the crankshaft is formed by the through hole, and the refrigerant gas and the refrigerating machine oil leaking from the inside of the housing to the outside of the seal member are It is discharged to the outside of the housing through the communication passage formed by the through hole provided in the. Therefore, the refrigerant gas leaked to the outside of the seal member and the oil component contained in the refrigerating machine oil do not act on the clutch through the gap between the components of the auxiliary bearing and do not hinder the operation of the clutch. Power can be reliably transmitted to the crankshaft side via the clutch, and desired compression performance can be obtained. Further, since the refrigerant gas does not pass through the gap of the sub bearing, the lubricating oil of the sub bearing is not exhausted, and therefore the sub bearing can be prevented from being damaged. Further, since the crankshaft is provided with a through hole as a hole for discharging the leaked gas, it is possible to prevent an increase in the entire length of the compressor.

Further, the same effect can be obtained when the communication passage provided in the crankshaft is formed by the notch portion, and the refrigerant gas and the refrigerating machine oil leaking from the inside of the housing to the outside of the seal member are It is discharged to the outside of the housing through the communication passage formed by the cutout portion provided in. Therefore, the refrigerant gas leaked to the outside of the seal member and the oil component contained in the refrigerating machine oil do not act on the clutch through the gap between the components of the auxiliary bearing and do not hinder the operation of the clutch. Power can be reliably transmitted to the crankshaft side via the clutch, and a desired compression capacity can be obtained. Further, since the refrigerant gas does not pass through the gap of the sub bearing, the lubricating oil of the sub bearing is not exhausted, and therefore the sub bearing can be prevented from being damaged.
Further, since the crankshaft is provided with a notch as a hole for discharging the leaked gas, it is possible to prevent an increase in the total length of the compressor.

Further, the same effect can be obtained when the communication passage provided in the inner diameter cylindrical portion of the second housing is constituted by a groove or a through hole or a combination of the groove and the through hole. Refrigerant gas and refrigerating machine oil that have leaked to the outer portion of the seal member are discharged to the outside of the housing through a communication passage formed by a groove provided in the housing. Therefore, the refrigerant gas leaked to the outside of the seal member and the oil component contained in the refrigerating machine oil do not act on the clutch through the gap between the components of the auxiliary bearing and do not hinder the operation of the clutch. Power can be reliably transmitted to the crankshaft side via the clutch, and desired compression performance can be obtained. Further, since the refrigerant gas does not pass through the gap of the sub bearing, the lubricating oil of the sub bearing is not exhausted, and therefore the sub bearing can be prevented from being damaged. Further, since the groove or the through hole as the hole for discharging the leaked gas is provided in the inner diameter cylinder portion of the second housing, it is possible to prevent the increase in the total length of the compressor.

Further, when the second housing is molded by casting, a groove is formed in the inner diameter cylindrical portion of the second housing without separately performing the step of forming the hole or groove for discharging the leaked gas. It can be formed at the same time. Therefore, the manufacturing process of the compressor can be reduced.

When a groove is provided on the outer peripheral surface of the inner diameter cylindrical portion of the second housing, part of the outer peripheral surface of the cylinder is molded into an open circular cross section to improve the workability and to provide a space for the groove. It can be easily molded.

[Brief description of drawings]

FIG. 1 is a cross-sectional view showing an entire first embodiment of a scroll compressor according to the present invention.

FIG. 2 is a partially enlarged view of FIG.

FIG. 3 is a partially enlarged sectional view showing a second embodiment of the scroll compressor according to the present invention.

FIG. 4 is a partially enlarged sectional view showing a third embodiment of the scroll compressor according to the present invention.

FIG. 5 is a partially enlarged sectional view showing a fourth embodiment of the scroll compressor according to the present invention.

FIG. 6 is a partially enlarged sectional view showing a fifth embodiment of the scroll compressor according to the present invention.

7 is a perspective view of a main part showing a configuration example of an inner diameter tubular portion in FIG.

FIG. 8 is a cross-sectional view of essential parts showing a modified example of the groove portion provided in the inner diameter tubular portion in the fifth embodiment shown in FIG. 6.

FIG. 9 is a cross-sectional view showing an entire example of a conventional scroll compressor.

[Explanation of symbols] 1 Scroll type compressor (compressor) 2 housing 3 Housing body (first housing) 4 Lid member (second housing) 6 Boss (inner diameter tube) 10 crankshaft 14 Leakage gas discharge path (communication path) 15, 18, 19b Through hole 16 Notch 17, 19a groove 20 Seal member 25 clutch

─────────────────────────────────────────────────── ─── Continuation of front page (51) Int.Cl. ⁷ Identification code FI theme code (reference) F04C 29/02 F04C 29/02 ZF term (reference) 3H003 AA05 AB07 AC03 AD01 BC01 BD09 CA00 CD01 CD05 3H029 AA02 AA17 AB03 BB01 BB16 BB35 BB47 CC08 CC16 CC32 3H039 AA02 AA12 BB11 BB15 BB16 BB25 CC13 CC27 CC40 CC41

Claims (10)

[Claims] 1. A compressor that forms an outline of a compressor by hermetically connecting a first housing and a second housing, wherein a compression mechanism for compressing a working fluid is installed in the first housing. A main bearing and a sub bearing are installed in this order from the joint surface side with the first housing in the inner diameter tubular portion of the second housing, and the crank shaft fixedly supported by the main bearing and the sub bearing is installed. A crankshaft, one end of which is connected to the compression mechanism, and the other end of which is provided with a clutch that transmits or disconnects power from a drive source that rotationally drives the crankshaft to the crankshaft, and The crankshaft is a compressor in which the inside and the outside of the compressor are sealed by a ring-shaped seal member installed between the main bearing and the sub bearing of the inner diameter tubular portion of the second housing. Member and the sub Compressor, wherein a communication passage formed in the crank shaft for communicating the space and the second housing external composed inside diameter tubular portion of the the receiving second housing. 2. The compressor according to claim 1, wherein the space formed by the seal member, the auxiliary bearing, and the inner diameter cylindrical portion of the second housing communicates with the outside of the second housing. Is a compressor comprising at least one through hole provided in the crankshaft. 3. The compressor according to claim 1, wherein the space formed by the seal member, the auxiliary bearing, and the inner diameter tubular portion of the second housing communicates with the outside of the second housing. Is a notch provided in an outer diameter portion of the crankshaft. 4. A compressor, which forms an outline of a compressor by hermetically connecting a first housing and a second housing, wherein a compression mechanism for compressing a working fluid is installed in the first housing. A main bearing and a sub bearing are installed in this order from the joint surface side with the first housing in the inner diameter tubular portion of the second housing, and the crank shaft fixedly supported by the main bearing and the sub bearing is installed. A crankshaft, one end of which is connected to the compression mechanism, and the other end of which is provided with a clutch that transmits or disconnects power from a drive source that rotationally drives the crankshaft to the crankshaft, and The crankshaft is a compressor in which the inside and the outside of the compressor are sealed by a ring-shaped seal member installed between the main bearing and the sub bearing of the inner diameter tubular portion of the second housing. Member and the sub Compressor, characterized in that a communicating passage connecting the end faces outside of the receiving and space formed by the inside diameter tubular portion of the second housing and the second housing to the inside diameter tubular portion of the second housing. 5. The compressor according to claim 4, wherein the space formed by the seal member, the auxiliary bearing, and the inner diameter tubular portion of the second housing communicates with the outside of the second housing. Is a groove or a through hole provided in the inner diameter cylindrical portion of the second housing. 6. The compressor according to claim 5, wherein the second housing is a cast product made of a material such as an aluminum alloy or cast iron, and is provided in an inner diameter cylinder portion of the second housing. The compressor is characterized in that the groove is formed by casting. 7. A compressor that forms an outline of a compressor by hermetically connecting a first housing and a second housing, wherein a compression mechanism for compressing a working fluid is installed in the first housing. A main bearing and a sub bearing are installed in this order from the joint surface side with the first housing in the inner diameter tubular portion of the second housing, and the crank shaft fixedly supported by the main bearing and the sub bearing is installed. A crankshaft, one end of which is connected to the compression mechanism, and the other end of which is provided with a clutch that transmits or disconnects power from a drive source that rotationally drives the crankshaft to the crankshaft, and The crankshaft is a compressor in which the inside and the outside of the compressor are sealed by a ring-shaped seal member installed between the main bearing and the sub bearing of the inner diameter tubular portion of the second housing. Member and the sub A compression passage, characterized in that a communication passage is provided in the inner diameter tubular portion of the second housing to connect the space formed by the receiving portion and the inner diameter tubular portion of the second housing to the outer circumference of the inner diameter tubular portion of the second housing. Machine. 8. The compressor according to claim 7, wherein a space formed by the seal member, the auxiliary bearing, and an inner diameter tubular portion of the second housing and an outer circumference of the inner diameter tubular portion of the second housing are provided. The compressor is characterized in that the communicating passage is formed of a groove provided on the outer peripheral surface of the inner diameter cylindrical portion of the second housing and a through hole communicating with the groove from the inner peripheral surface of the inner diameter cylindrical portion. 9. The compressor according to claim 8, wherein the second housing is a cast product made of a material such as an aluminum alloy or cast iron, and the outer peripheral surface of the inner diameter cylindrical portion of the second housing is provided. The compressor is characterized in that the provided groove is formed by casting. 10. The compressor according to claim 8, wherein the groove provided on the outer peripheral surface of the inner diameter tubular portion of the second housing comprises:
A compressor characterized in that a part of an outer peripheral surface of a cylinder is molded into an open circular cross section.