JP2530842Y2 - Oil-cooled compressor - Google Patents

Description

[Detailed description of the invention]

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an oil-cooled compressor in which temperature-adjusted oil is injected into a gas compression space in a compressor body.

[0002]

2. Description of the Related Art A conventional oil-cooled compressor shown in FIG.
The suction passage 13 provided with the oil separation and recovery device 1 is provided on the discharge side.
4 is connected to the discharge channel 15. The lower part of the oil separator / collector 14 is an oil sump 16 from which a temperature control valve 17 is branched, where the first flow path 19 passing through an oil cooler 18 and an oil cooler 18 are connected. Second not going through
The oil is branched into a flow path 20, and the two flow paths join at the outlet side of the oil cooler 18, and the oil reaches a lubricating point such as a gas compression space, a bearing, and a shaft seal (not shown) in the compressor main body 11. Supply channel 2
1 is provided. Oil separation and recovery device 14 in oil supply passage 21
A temperature switch 22 is provided in a portion between the temperature control valve 17 and the temperature control valve 17 so that the temperature of the oil can be detected.
Conversely, the higher the detected oil temperature is, the larger the cross-sectional area between the A and C ports is, compared to the cross-sectional area between the B-ports. Is controllable with respect to the temperature control valve 17 so that is increased.

[0003] In addition to lubrication at the lubricating point, oil injected for cooling and sealing, especially in the gas compression space, is finally supplied to the oil reservoir 1 in the oil separator / collector 14.
6, and the oil is sent again from the oil supply flow path 21 to the above-described lubrication point. When the temperature of the oil injected into the lubrication point falls below a certain temperature, the suction passage 1
The steam contained in the gas sucked into the compressor main body 11 from the compressor 3 is condensed and becomes drain water.
4 and is in an undesirable state. In order to prevent this, when the temperature detected by the temperature switch 22 is high, the ports A and C of the temperature control valve 17 are set to the non-communication state, the ports A and B are set to the communication state, and the oil is cooled by the oil cooler 18.
While cooling at the same time, the lower the detected oil temperature, the smaller the cross-sectional area of the flow path between the A and B ports and the larger the cross-sectional area of the flow path between the A and C ports.
The oil flowing through zero is increased, the oil temperature is prevented from lowering, and the lubrication temperature is kept within a certain range.

As an example of the specific contents of the control of the temperature control valve 17, the detected temperature T ° C, the flow ratio between the A and B ports (%), the flow ratio between the A and C ports (%), and The following Table 1 shows the relationship between the oil temperature and the oil temperature.
It will be kept between 0 ° C.

[0005]

[Table 1]

[0006] The oil before the start of the compressor is in a low temperature state.
The flow path between the A and B ports for guiding the oil to the flow path 19 is in a closed state.
%, The flow ratio between the A and C ports is 100%. In general, the temperature control valve 17 has a time constant after detecting the oil temperature T ° C and taking a certain period of time before actually shifting to the set flow distribution state.

[0007]

In the conventional compressor described above, at start-up, 100% of the oil flows through the second flow path 20, and thereafter the oil temperature rises rapidly. As the oil temperature rises, the flow path between the A and B ports starts to open. Incidentally, the flow path resistance of the first flow path 19 is generally larger than that of the second flow path 20. For this reason, even if the cross-sectional area of the flow path between the A and B ports is equal to the cross-sectional area of the flow path between the A and C ports, the flow rate of the oil in the first flow path 19 is small, and the flow rate between the A and C ports is small. Only when the road is almost closed does the oil start flowing to the oil cooler 18. As a result, when the compressor is started, the oil temperature becomes too high, and the signal from the temperature switch 22 causes a problem that the compressor is emergency stopped. The present invention has been made to solve such a conventional problem, and for example, at the time of startup, an oil-cooled type that can prevent an excessive rise in oil temperature and eliminate the occurrence of an emergency stop. It is intended to provide a compressor.

[0008]

In order to solve the above problems, the present invention relates to a compressor body, an oil separation and recovery device provided on the discharge side, and an oil reservoir at the lower portion of the oil separation and recovery device. It reaches the temperature control valve, branches here, and branches into a first flow path that passes through the oil cooler and a second flow path that does not pass through the oil cooler. In an oil-cooled compressor having a gas supply space in the compressor body, an oil supply passage extending to a lubrication point such as a bearing, a shaft seal portion, and the like,
The second flow path is formed so as to be able to restrict the flow rate as compared with the case where the first flow path has the same flow path cross-sectional area.

[0009]

With the above construction, the flow resistances of the first flow path and the second flow path are balanced.

[0010]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention will be described below with reference to the drawings. FIG. 1 shows an oil-cooled compressor according to a first embodiment of the present invention, which is substantially the same as the compressor shown in FIG. 5 except that an orifice 1 is provided in a second flow path 20. Parts that are the same and that are common to each other are given the same reference numerals and description thereof is omitted. In the first embodiment, the orifice 1
Is provided, the flow rate in the second flow path 20 is limited, and when the flow path between the A and B ports of the temperature control valve 17 is opened, the flow of oil into the oil cooler 18 is not delayed. It is. In this way, for example, when the compressor is started, it is possible to prevent an excessive rise in the oil temperature and an emergency stop of the compressor accompanying the oil temperature.

FIG. 2 shows the change in the oil temperature detected by the temperature switch 22 immediately after the start of the compressor in the case of the first embodiment. The curve shown by the solid line in this embodiment is the two-dot chain line. The curve shown by indicates the temperature change when the orifice 1 is not provided. As can be seen from the figure, when the orifice 1 is not provided, the oil temperature _immediately exceeds the temperature switch set temperature T _o after startup, whereas in the present embodiment, the oil cooler 18 Oil flows without delay and the oil temperature is kept low.

FIG. 3 shows an oil-cooled compressor according to a second embodiment of the present invention. The compressor shown in FIG. 1 is different from the compressor shown in FIG. The other parts are substantially the same except that a first flow path 19a having a large pipe diameter is provided, and the common parts are denoted by the same reference numerals and description thereof is omitted. By forming the second embodiment in this manner, the flow resistance per unit length of the first flow path 19a is reduced, and the flow paths of the first flow path 19a and the second flow path 20 as a whole are reduced. The resistance is balanced, and as a result, as in the first embodiment, there is no delay in the flow of oil into the oil cooler 18.

FIG. 4 shows an oil-cooled compressor according to a third embodiment of the present invention, which is different from the compressor shown in FIG. 1 in that a flow control valve 2 is provided in the second flow passage 20 instead of the orifice 1. Except for
The other parts are substantially the same, and the parts common to each other are denoted by the same reference numerals and description thereof is omitted. In the third embodiment, the flow rate of the oil in the second flow path 20 is limited by the temperature control valve 2 so that the oil can easily flow toward the first flow path. Is caused.

[0014]

As is apparent from the above description, according to the present invention, the temperature of the compressor body, the oil separation / recovery device provided on the discharge side, and the temperature of the oil reservoir at the lower part of the oil separation / recovery device are measured. It reaches the control valve, where it branches off and the first through the oil cooler
It branches into a flow path and a second flow path that does not pass through the oil cooler, and the two flow paths join at the outlet side of the oil cooler to form a gas compression space, a bearing, and a shaft seal in the compressor body. In the oil-cooled compressor having an oil supply flow path extending to an oil injection point such as a part, the flow rate of the second flow path can be restricted as compared with the case where the first flow path has the same flow path cross-sectional area. It is formed in.

For this reason, the flow resistance of the first flow path and the flow resistance of the second flow path are balanced, for example, to prevent the oil temperature from excessively rising at the time of startup and to eliminate the occurrence of an emergency stop. This has the effect that it becomes possible.

[Brief description of the drawings]

FIG. 1 is an overall configuration diagram of an oil-cooled compressor according to a first embodiment of the present invention.

FIG. 2 is a diagram showing a change in oil temperature after the compressor shown in FIG. 1 is started.

FIG. 3 is an overall configuration diagram of an oil-cooled compressor according to a second embodiment of the present invention.

FIG. 4 is an overall configuration diagram of an oil-cooled compressor according to a third embodiment of the present invention.

FIG. 5 is an overall configuration diagram of a conventional oil-cooled compressor.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Orifice 2 Flow control valve 11 Compressor main body 14 Oil separation and recovery unit 15 Discharge flow path 16 Oil reservoir 17 Temperature control valve 18 Oil cooler 19, 19a First flow path 20 Second flow path 21 Oil supply flow path

Claims (1)

(57) [Scope of request for utility model registration] 1. A compressor body, an oil separation / recovery device provided on the discharge side, and an oil reservoir at a lower portion of the oil separation / recovery device to a temperature control valve. And a second flow path that does not pass through the oil cooler, and the two flow paths join at the outlet side of the oil cooler to form a gas compression space portion and a bearing in the compressor body. , An oil-cooled compressor having an oil supply passage to an oiling point such as a shaft seal portion,
An oil-cooled compressor, wherein the second flow path is formed so as to be able to restrict a flow rate as compared with a case where the second flow path has the same flow path cross-sectional area as the first flow path.