JP3882262B2 - Fluid machine with wet clutch device - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a fluid machine whose operation is interrupted by a wet clutch device, and is suitable, for example, for a refrigerant compressor of an air conditioner for automobiles.
[0002]
[Prior art]
Conventionally, JP-A-63-135619 discloses an example in which an oil pump is used to obtain a pressing force for pressing a friction plate in a refrigerant compressor using a wet multi-plate clutch.
[0003]
[Problems to be solved by the invention]
The oil pump used in this example is configured to suck in the oil stored in the oil reservoir in the compressor, so that a sufficient amount of oil in the oil reservoir can be stored due to removal by a refrigerant or the like. There is a problem that the clutch can not be engaged when not.
[0004]
For this reason, it is conceivable to separate the pressure generating unit from the compressor. However, this measure causes an increase in the size and cost of the fluid machine, such as requiring an oil pump drive source.
The present invention has been made in view of the above points, and an object of the present invention is to obtain a stable pressure source without causing an increase in size of a fluid machine and to reliably operate a wet clutch device.
[0005]
[Means for Solving the Problems]
In order to achieve the above object, according to the first to third aspects of the present invention, the driven clutch plate (11) rotated by the rotation of the drive shaft (5) is disposed opposite to the driven clutch plate (11). The main pump (1) is connected to the clutch plate (11),
A clutch plate displacing means (8) for connecting the drive side clutch plate (12) and the driven side clutch plate (11) by pressing the clutch plates (11, 12) and connecting them together, and a drive shaft ( 5) The pressure control device (15, 21a) that causes the clutch plate displacing means (8) to be pressed or released to both clutch plates (11, 12) by transmitting the rotational power from 5) and increasing or decreasing the pressure of the liquid working fluid. , 23, 25), and the fluid circuit communicating the pressure control device (15, 21a, 23, 25) and the clutch plate displacement means (8) is configured independently of the fluid circuit of the main pump (1). It is characterized by that.
[0006]
According to this, since the fluid circuit on the pressure control device side is a circuit independent of the main pump (1), a stable pressure source is always provided regardless of the amount of working fluid on the main pump (1) side. So that the wet clutch device (30) can always be operated reliably.
Moreover, since the pressure control device of the present invention operates by transmitting the rotational power of the drive shaft (5) of the main pump (1), it can be integrated with the main pump (1). 1) and the wet-type clutch device (30), the effect that can contribute to miniaturization of the whole fluid machine and cost reduction is great.
[0007]
According to the pressure control device of the present invention, the auxiliary pump (15) for pumping the liquid by the rotational power transmitted from the drive shaft (5) and the discharge fluid of the auxiliary pump (15) as described in claim 2 Valve means (25) for switching the flow path, a relief valve (21a) for controlling the liquid working fluid of the auxiliary pump (15) to a predetermined pressure, and the amount of liquid accompanying the pressure increase / decrease of the working fluid It can implement suitably by setting it as the structure provided with the liquid reservoir part (23) which absorbs an increase / decrease.
[0008]
In the invention according to claim 3, the auxiliary pump (15) is a reciprocating pump having a reciprocating piston (15a), and the drive shaft (5) is for driving the reciprocating piston (15a). An eccentric part (5a) is provided. Thereby, the auxiliary pump (15) can be directly driven by the drive shaft (5), and the auxiliary pump (15) with a built-in fluid machine can have a very simple configuration.
[0009]
In addition, the code | symbol in the parenthesis attached | subjected to each said means and each means as described in a claim shows the correspondence with the specific means as described in embodiment mentioned later.
[0010]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, embodiments of the present invention will be described with reference to the drawings.
FIG. 1 shows an embodiment in which the present invention is used in a refrigerant compressor of an air conditioning compressor for automobiles. In FIG. 1, the compressor 1 forms the main pump of the present invention, and is a scroll type. It is a known rotary compressor such as a swash plate type, and the type is not particularly selected.
[0011]
A drive shaft 5 is rotatably supported at the center of the front housing 2 of the compressor 1, and one end (the left end portion in the drawing) of the drive shaft 5 is an opening formed at one end portion of the front housing 2. It protrudes to the outside through 2a. A pulley 6 of a power transmission mechanism is connected to a projecting end portion of the drive shaft 5 by a fastening bolt 7, and the drive shaft 5 is connected to a rotation output portion (crank pulley) of an automobile engine via the power transmission mechanism. Yes. Therefore, the drive shaft 5 is always rotated by the engine rotational power when the automobile engine is operated.
[0012]
A bearing 3 is disposed between the outer peripheral surface of the drive shaft 5 and the inner peripheral surface of the opening 2a of the front housing 2, and one end side of the drive shaft 5 is rotatably supported. Further, a shaft seal device 4 is provided between the outer peripheral surface of the drive shaft 5 and the inner peripheral surface of the opening 2a of the front housing 2 to prevent the refrigerant inside the front housing 2 from leaking to the outside.
[0013]
A driven shaft 13 is disposed on the other end side (the right side in the figure) of the drive shaft 5, and the driven shaft 13 is rotatably supported by the bearing 10 with respect to the front housing 2. The other end of the drive shaft 5 is supported by the bearing 14 so as to be rotatable with respect to the driven shaft 13. The driven shaft 13 is integrally formed with an enlarged cylindrical portion 13a and an eccentric crank portion 13b, and the eccentric crank portion 13b drives a compression mechanism of the compressor 1 (in this example, a movable scroll of a scroll type compression mechanism).
[0014]
A wet multi-plate friction clutch device 30 is disposed between the inner peripheral surface of the enlarged cylindrical portion 13 a of the driven shaft 13 and the outer peripheral surface on the other end side of the drive shaft 5. The clutch device 30 is provided with a drive side clutch plate 12 and a driven side clutch plate 11 formed in a disc shape. The drive-side clutch plate 12 is slidable in the axial direction with respect to the outer peripheral surface on the other end side of the drive shaft 5 and is integrally locked in the rotational direction. The driven clutch plate 11 is slidable in the axial direction with respect to the inner peripheral surface of the enlarged cylindrical portion 13a of the driven shaft 13, and is integrally locked in the rotational direction.
[0015]
A large number of the drive side clutch plates 12 and the driven side clutch plates 11 are alternately arranged, and one of the clutch plates 11 and 12 is interposed by a control piston 8 (clutch plate displacing means) with a thrust bearing 9 interposed therebetween. One of them is displaced toward the other, whereby both the clutch plates 11 and 12 are crimped and connected together. On the other hand, when released from the pressing force from the control piston 8, both the clutch plates 11 and 12 are brought into the open state by the spring force of the spring means (not shown). The control piston 8 has a ring shape, is arranged concentrically with the drive shaft 5 at a predetermined interval from the outer peripheral surface of the drive shaft 5, and is controlled to the right in FIG. 1 by the control pressure applied to the back pressure chamber 8a. Displace to
[0016]
Reference numeral 15 denotes an auxiliary pump according to the present invention. In this example, a reciprocating pump having a reciprocating piston 15a is used. An eccentric portion 5 a is integrally formed on the drive shaft 5, and the reciprocating piston 15 a moves downward in FIG. 1 against the spring force of the coil spring 16 by the amount of eccentricity of the eccentric portion 5 a. On the contrary, when the eccentric amount of the eccentric portion 5a is reduced, the reciprocating piston 15a is moved upward in FIG. 1 by the spring force of the coil spring 16. Accordingly, the reciprocating piston 15a reciprocates in the vertical direction in FIG. 1 by the coil spring 16 and the eccentric portion 5a.
[0017]
The reciprocating piston 15a is driven by the eccentric portion 5a of the drive shaft 5 disposed in the atmosphere of the refrigerant gas that is the working fluid of the compressor 1, but is provided on the outer periphery of the reciprocating piston 15a. The reciprocating piston 15a is well sealed from the compressor 1 by the sealing mechanism (not shown). Thereby, the hydraulic circuit (fluid circuit) of the pressure control device including the auxiliary pump 15 is configured independently of the refrigerant circuit (fluid circuit) on the compressor 1 side. Therefore, the refrigerant on the compressor 1 side does not enter or leave the hydraulic circuit of the pressure control device.
[0018]
The reciprocating piston 15a is driven by the eccentric portion 5a of the drive shaft 5 to perform reciprocating motion, whereby oil (liquid working fluid) stored in the reservoir 23 is passed through the suction passage 27, the piston inner passage 15b, and the suction valve 17a. And sucked into the working chamber 15c.
Here, the reservoir 23 functions as a liquid reservoir that absorbs an increase or decrease in the amount of oil in the hydraulic circuit caused by the pressure increase or decrease of the oil, and a piston 23a is accommodated inside the reservoir 23. The weak spring force of the coil spring 23a acts on the piston 23a. Therefore, the piston 23a can be displaced by the weak pressure of the oil flowing into the reservoir 23, and the internal pressure of the reservoir 23 is always sufficient to release the pressing force of the control piston 8 due to the displacement of the piston 23b. It is kept at an extremely low pressure. Note that the inside of the reservoir 23 may be open to the atmosphere, and the atmospheric pressure may be set.
[0019]
Oil discharged from the working chamber 15c of the reciprocating piston 15a is discharged to the discharge passage 20 through the discharge valve 19a. Here, 17b and 19b are coil springs that act on the suction valve 17a and the discharge valve 19a, respectively.
The discharge passage 20 communicates with the back pressure chamber 8a of the control piston 8 and communicates with the electromagnetic valve 25 and the relief valve 21a. The electromagnetic valve 25 is a valve means for switching the clutch device, that is, the operation of the compressor 1, and is energized by the control device 26 of the automotive air conditioner, so that the back pressure chamber 8 a and the reservoir 23 are switched. The flow path between is opened and closed.
[0020]
The relief valve 21 opens at a set pressure that is higher by a predetermined value than the predetermined pressure required to obtain the required pressing force of the control piston 8. Reference numeral 21 a denotes a coil spring that sets the valve opening pressure of the relief valve 21. In the present embodiment, the auxiliary pump 15, the relief valve 21, the reservoir 23, and the electromagnetic valve 25 constitute a pressure control device.
[0021]
Next, the operation of this embodiment in the above configuration will be described. Since the drive shaft 5 is connected to a rotation output portion (crank pulley) of the automobile engine, the drive shaft 5 is always rotated during operation of the automobile engine. Accordingly, as the eccentric portion 5a of the drive shaft 5 rotates, the auxiliary pump 15 is always operated, and the oil is sucked from the reservoir 23 through the suction passage 27, compressed, and discharged.
[0022]
Now, when a compression operation signal is output from the control device 26, the signal from the control device 26 is received, and the electromagnetic valve 25 is closed as shown in FIG. Then, the back pressure chamber 8a and the reservoir 23 are blocked, and the discharge pressure of the auxiliary pump 15 is applied to the back pressure chamber 8a of the control piston 8.
At this time, since the oil (working fluid) discharged from the auxiliary pump 15 is liquid and incompressible, there is a possibility that the pressure increases abnormally when the hydraulic circuit system is sealed by the electromagnetic valve 25. The relief valve 21 is provided in parallel with the relief valve 21, and the relief valve 21 controls the discharge pressure of the auxiliary pump 15 to be a predetermined pressure.
[0023]
When the discharge pressure of the auxiliary pump 15 is applied to the back pressure chamber 8a, the control piston 8 moves in the right direction in the figure, so that the right side pressure in the figure acts on the driven side clutch plate 11.
As a result, the driven side clutch plate 11 is crimped to the drive side clutch plate 12, and the both clutch plates 11 and 12 are integrally connected. Accordingly, the rotation of the drive shaft 5 is transmitted to the driven shaft 13 via the clutch device 30, and the driven shaft 13 rotates, so that the compressor 1 performs a compression operation.
[0024]
Next, when a compression stop signal is issued from the control device 26, the signal from the control device 26 is received, and the electromagnetic valve 25 is opened as shown in FIG. Then, the back pressure chamber 8a and the reservoir 23 communicate with each other, so that the back pressure chamber 8a of the control piston 8 is released from the discharge pressure of the auxiliary pump 15.
As a result, the pressing force to the clutch device 30 by the control piston 8 is eliminated, and the clutch plates 11 and 12 of the clutch device 30 are separated from each other by spring means (not shown). The rotation transmission to 13 is cut off, and the operation of the compressor 1 is stopped.
[0025]
As described above, according to the present embodiment, the pressure control device provided as a pressure source for connecting the clutch device 30 is a hydraulic circuit independent of the compressor 1. It can always be used as a stable pressure source regardless of the amount of oil in the section, and the clutch device 30 can always be operated reliably.
[0026]
(Other embodiments)
In the above embodiment, a reciprocating pump using a reciprocating piston 15a is used as the auxiliary pump 15. However, as the auxiliary pump 15 that operates using the rotation of the drive shaft 5 as a power source, a rolling piston type is also available. A trochoid pump or the like can also be used.
[0027]
Moreover, although the case where this invention was used for the refrigerant compressor of the air conditioner for motor vehicles was demonstrated in the said embodiment, this invention is widely applicable to the fluid machine of various uses besides a refrigerant compressor.
[Brief description of the drawings]
FIG. 1 is a longitudinal sectional view showing an embodiment of the present invention.
2A is a hydraulic circuit diagram showing a connected state of the wet clutch device of the embodiment, and FIG. 2B is a hydraulic circuit diagram showing a disengaged state of the wet clutch device of the embodiment.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 ... Compressor (main pump), 5 ... Drive shaft, 5a ... Eccentric part,
8 ... control piston (clutch plate displacement means), 11 ... driven side clutch plate,
12 ... Drive side clutch plate, 13 ... Drive shaft, 15 ... Auxiliary pump,
15a ... reciprocating piston, 21a ... relief valve, 23 ... reservoir,
25 ... Solenoid valve.

Claims (3)

A drive shaft (5) that is rotated by rotation power transmitted from a drive source;
A drive side clutch plate (12) rotated by rotation of the drive shaft (5);
A driven side clutch plate (11) that is disposed opposite to the drive side clutch plate (12) and is capable of rotating integrally with the drive side clutch plate (12) when crimped to the drive side clutch plate (12);
A main pump (1) coupled to the driven side clutch plate (11), to which rotational power is transmitted through the driven side clutch plate (11) and performing a pumping action;
Clutch plate displacing means (8) for applying a pressing force to the driving side clutch plate (12) and the driven side clutch plate (11) to crimp the clutch plates (11, 12) and to connect them together;
Pressure that causes the clutch plate displacing means (8) to be pressed or released to the clutch plates (11, 12) by transmitting rotational power from the drive shaft (5) and increasing or decreasing the pressure of the liquid working fluid. While having a control device (15, 21a, 23, 25),
A wet circuit characterized in that a fluid circuit communicating the pressure control device (15, 21a, 23, 25) and the clutch plate displacing means (8) is configured independently of the fluid circuit of the main pump (1). A fluid machine equipped with a clutch device. The pressure control device includes an auxiliary pump (15) that receives rotational power from the drive shaft (5) and pumps liquid.
Valve means (25) for switching the flow path of the discharge fluid of the auxiliary pump (15);
A relief valve (21a) for controlling the liquid working fluid of the auxiliary pump (15) to a predetermined pressure;
The fluid machine provided with the wet clutch according to claim 1, further comprising a liquid reservoir (23) that absorbs an increase or decrease in the amount of liquid that accompanies pressure increase or pressure reduction of the working fluid. The auxiliary pump (15) is a reciprocating type pump having a reciprocating piston (15a),
The fluid machine with a wet clutch according to claim 2, wherein the drive shaft (5) is provided with an eccentric portion (5a) for driving the reciprocating piston (15a).

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