JP3830599B2 - Speed limiter - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to driving of auxiliary equipment for automobiles, and more particularly to an output rotational speed limiting device for auxiliary equipment that uses rotational power from an output shaft of an engine.
[0002]
[Prior art]
For example, conventionally, the driving of automobile auxiliary equipment (PS pump, generator, cooler compressor) is carried out by attaching a pulley to the engine output shaft (crankshaft) and auxiliary equipment. It is carried out by a belt transmission device that rotates the auxiliary machinery by belt friction between the pulley and the belt, and the auxiliary machinery is driven by this belt transmission device. The engine is rotated at a speed proportional to the engine speed (approximately 600 to 7000 rpm), and is sufficiently configured to function even at low speeds (idling).
[0003]
[Problems to be solved by the invention]
By the way, in the driving of the auxiliary machines by the conventional belt transmission device, when the engine rotates at high speed, the auxiliary machines are belted on a pulley attached to the output shaft (crankshaft) of the engine, Therefore, there is a problem that unnecessary output is lost in a high-speed rotation region.
[0004]
Furthermore, although the auxiliary machines are individually designed to reduce energy loss, the engine speed is about 600 to 7000 rpm and a wide-range speed, so that the auxiliary machines are low speed to high speed. It must have a durable structure with sufficient consideration for seals, bearings, high temperature, and pressure resistance so that it can withstand rotation, so the price is significantly higher due to the need for specifications that support high-speed rotation. As a result, there was a problem that the cost could not be reduced.
[0005]
Therefore, the present invention requires a specification corresponding to the high-speed rotation of the auxiliary equipment by limiting the rotational speed of the auxiliary machinery to a fixed value so that the rotational speed of the auxiliary machinery does not exceed the predetermined rotational speed with respect to the high-speed rotation of the engine. To reduce costs, simplify, and reduce costs.
[0006]
[Means for Solving the Problems]
In the first invention, a body , a plate fastened to the body via a seal member, a rotating shaft that is rotatably supported through the plate, and coupled to the rotating shaft in the body An eccentric cam interposed in the cam chamber formed in the shaft, a piston interlocking with the eccentric cam, a cylinder radially formed around the rotation shaft in a body in which the piston is slidably inserted, and the other end of the cylinder And a radial piston pump and a motor configured to supply and discharge hydraulic oil in the expansion chamber by piston operation, the radial piston pump and the motor being connected to the cam chamber. connected via the radial piston pump and motor - to limit the rotational speed of the motor - motor by regulating the suction of the radial piston pump communicates via a passage aperture for the cam chamber of the motor.
[0008]
In the second invention, the radial piston pump and the motor are formed on the other end side of the cylinder with an enlarged diameter portion, and the enlarged diameter portion is sealed with a seal member and inserted into a step diameter portion. A plug, a diameter expansion chamber in which a diameter expansion portion is partitioned by the plug, a passage communicating with a cylinder having a phase delay of 90 ° radially around the rotation axis from the diameter expansion chamber, and the passage And a piston having an annular groove for inserting and closing a suction port and a discharge port provided in a cylinder having a phase difference of 90 ° and one end of the piston on the outer periphery of the eccentric cam. The spring is attached to the step diameter portion of the plug that is urged so as to be in sliding contact. Cylinder suction port with 90 ° phase lag difference Communication with, while the enlarged chamber is reduced, the passage discharge port of the cylinder with a difference of 90 ° phase lag - configured to preparative communication with.
[0009]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, embodiments of the present invention will be described with reference to the drawings. As shown in FIG. 1, in the rotation speed limiting device according to this embodiment, the main body 1 is fastened to the body 2 and the body 2 with bolts 18, and the plates 3 a and 3 b through the seal member 20. And is fastened to the mounting angle 4 with bolts 19.
[0010]
A radial piston pump (hereinafter referred to as a pump) 5 and a radial piston motor (hereinafter referred to as a motor) 6 are interposed in the main body 1.
[0011]
The pump 5 is rotatably supported by a bearing 7a and a needle bearing 7c provided on the body 2, and is mounted with a rotating shaft 9a sealed by a seal member 8a provided on the plate 3a. ing.
[0012]
One end of the rotating shaft 9a is directly connected to an engine (not shown).
[0013]
An eccentric cam 10a is integrally formed on the rotary shaft 9a, and a bearing 11a is rotatably fitted on the outer periphery 10c of the eccentric cam 10a, and is accommodated in a cam chamber 12a formed on the body 2. Yes.
[0014]
As shown in FIG. 2, first to fourth cylinders 13a, 13b, 13c, and 13d having a phase difference of 90 ° radially about the rotation shaft 9a are formed on the body 2 outside the cam chamber 12a. The
[0015]
These cylinders 13a, 13b, 13c, 13d are provided with suction ports 14a, 14b, 14c, 14d and discharge ports 15a, 15b, 15c, 15d provided facing the cam chamber 12a. Expanded portions 21a, 21b, 21c, and 21d are formed on the other end sides of 13a, 13b, 13c, and 13d.
[0016]
Plugs 23a, 23b, 23c, and 23d sealed with a seal member 22 are screwed into the enlarged diameter portions 21a, 21b, 21c, and 21d, and the enlarged diameter portions 21a, 21b are connected by the plugs 23a, 23b, 23c, and 23d. , 21c, 21d are divided into enlarged diameter chambers 24a, 24b, 24c, 24d.
[0017]
The diameter expansion chambers 24a, 24b, 24c, and 24d are ports 25d, 25a, 25b of cylinders 13d, 13a, 13b, and 13c having a difference in phase delay of 90 ° radially around the rotation shaft 9a . 25c communicates with passages 26a, 26b, 26c, and 26d.
[0018]
In the cylinders 13a, 13b, 13c, 13d, pistons 28a, 28b, 28c, 28d formed with annular grooves 27a, 27b, 27c, 27d on the outer periphery have one end in the cam chamber 12a and the other ends in the enlarged diameter chambers 24a, 24b. , 24c, 24d, and is inserted into the plugs 23a, 23b, 23c, 23d, and biased toward the eccentric cam 10a by a spring 30 interposed between the step diameter portions 29a, 29b, 29c, 29d of the plugs 23a, 23b, 23c, 23d. One end of the pistons 28a, 28b, 28c, 28d is brought into sliding contact with the outer periphery 11c of the bearing 11a provided on the eccentric cam 10a.
[0019]
On the other hand, the motor 6 has substantially the same configuration as the pump 5, and the same name and reference numeral will be given to the same configuration for explanation.
[0020]
The motor 6 is rotatably supported by a bearing 7b provided on the body 2 and a needle bearing 7d provided concentrically at the end of the rotary shaft 9a of the pump 5, and a motor provided on the plate 3b. A rotating shaft 9b sealed with a seal member 8b is mounted.
[0021]
An auxiliary machine (not shown) is directly connected to one end of the rotating shaft 9b.
[0022]
An eccentric cam 10b is integrally formed on the rotating shaft 9b, and a bearing 11b is rotatably fitted on the outer periphery 10d of the eccentric cam 10b so as to be accommodated in a cam chamber 12b formed on the body 2. Yes.
[0023]
As shown in FIG. 2, first to fourth cylinders 13a, 13b, 13c, and 13d having a phase difference of 90 ° radially around the rotation shaft 9b are formed on the body 2 outside the cam chamber 12b. The
[0024]
These cylinders 13a, 13b, 13c and 13d are provided with discharge ports 14a, 14b, 14c and 14d provided facing the cam chamber 12b, and supply ports 15a, 15b, 15c and 15d. Expanded portions 21a, 21b, 21c, and 21d are formed on the other end sides of 13a, 13b, 13c, and 13d.
[0025]
Plugs 23a, 23b, 23c, and 23d sealed with a seal member 22 are screwed into the enlarged diameter portions 21a, 21b, 21c, and 21d, and the enlarged diameter portions 21a, 21b are connected by the plugs 23a, 23b, 23c, and 23d. , 21c, 21d are divided into enlarged diameter chambers 24a, 24b, 24c, 24d.
[0026]
The diameter-enlarging chambers 24a, 24b, 24c, 24d are ports 25d, 25a, 25b of cylinders 13d, 13a, 13b, 13c , which have a radial phase difference of 90 ° about the rotating shaft 9b . 25c communicates with passages 26a, 26b, 26c, and 26d.
[0027]
In the cylinders 13a, 13b, 13c, 13d, pistons 28a, 28b, 28c, 28d having annular grooves 27a, 27b, 27c, 27d formed on the outer periphery have one end in the cam chamber 12b and the other end in the enlarged chambers 24a, 24b. 24c, 24d, and is inserted into the plugs 23a, 23b, 23c, 23d, and is biased toward the eccentric cam 10b by a spring 30 interposed between the step diameter portions 29a, 29b, 29c, 29d of the plugs 23a, 23b, 23c, 23d. One ends of the pistons 28a, 28b, 28c, and 28d are brought into sliding contact with the outer periphery 11d of the bearing 11b provided on the eccentric cam 10b.
[0028]
The discharge ports 15a, 15b, 15c and 15d of the pump 5 and the supply ports 15a, 15b, 15c and 15d of the motor 6 communicate with each other via a passage 16 formed in the body 2. The hydraulic oil discharged from the pump 5 is supplied to the supply ports 15a, 15b, 15c and 15d of the motor 6 through the passage 16, and the motor is discharged. Six discharge ports 14a, 14b, 14c and 14d are discharged to a cam chamber 12b serving as an oil reservoir.
[0029]
The eccentric cam chamber 12a of the pump 5 formed in the body 2 and the eccentric cam chamber 12b of the motor 6 communicate with each other via a throttle passage 17, and the diameter of the throttle passage 17 can be easily processed with a drill or the like. And change it.
[0030]
Next, the operation will be described.
When the pump 5 is driven by the power of the engine or the like and the rotating shaft 9a of the pump 5 rotates, the eccentric cam 10a coupled to the rotating shaft 9a rotates integrally, and the pistons 28a, 28b, 28c, and 28d are connected to the eccentric cam 10a. The bearing 11a fitted on the outer periphery 10c is slidably contacted and driven with a phase difference of 90 °, and reciprocates once every rotation of the rotating shaft 9a.
[0031]
When the first piston 28a is located at the bottom dead center, the first piston 28a closes the first suction port 14a, opens the first discharge port 15a, and opens the second expansion port. The diameter chamber 24b communicates with the first discharge port 15a through the second passage 26b, and the working oil in the diameter expansion chamber 24b flows out to the first discharge port 15a.
[0032]
The second piston 28b is in a neutral position, closes the second suction port 14b and the second discharge port 15b, and defines a third passage 26c communicating with the third diameter-expanding chamber 24c. Cut off.
[0033]
The third piston 28c is located at the top dead center, opens the third suction port 14c, closes the third discharge port 15c, and passes through the passage 26d from the fourth diameter expansion chamber 24d. The hydraulic fluid communicates with the third suction port 14c, and the hydraulic oil is sucked from the third suction port 14c into the fourth diameter expansion chamber 24d through the fourth passage 26d.
[0034]
The fourth piston 28d is in a neutral position, closes the fourth discharge port 15d and the fourth suction port 14d, and connects the first passage 26a communicating with the first diameter-expanding chamber 24a. Cut off.
[0035]
On the other hand, in the motor 6, when the first piston 28a is located at the bottom dead center, the first piston 28a closes the first discharge port 14a, and the first supply The port 15a is opened, and the first supply port 15a is communicated with the second diameter expansion chamber 24b and the second passage 26b, and the first supply port 15a is connected to the diameter expansion chamber 24b. Hydraulic oil is supplied.
[0036]
The second piston 28b is in a neutral position, closes the second discharge port 14b and the second supply port 15b, and establishes a third passage 26c communicating with the third diameter expansion chamber 24c. While shutting off, a reaction force is generated in the piston 28b by the hydraulic oil supplied to the diameter expansion chamber 24b, pressing the piston 28b and generating torque in the eccentric cam.
[0037]
The third piston 28c is located at the top dead center, opens the third discharge port 14c, closes the third supply port 15c, and passes through the passage 26d from the fourth diameter expansion chamber 24d. Then, the hydraulic fluid in the diameter expansion chamber 24d communicates with the third discharge port 14c and is discharged from the fourth diameter expansion chamber 24d to the third discharge port 14c through the fourth passage 26d.
[0038]
The fourth piston 28d is in a neutral position, closes the fourth supply port 15d and the fourth discharge port 14d, and establishes a first passage 26a communicating with the first diameter expansion chamber 24a. Cut off.
[0039]
In this way, hydraulic oil discharged from the discharge ports 15a, 15b, 15c, 15d of the pump 5 is supplied to the supply ports 15a, 15b, 15c, 15d of the motor 6 one after another. The reaction force is generated in each of the diameter expansion chambers 24a, 24b, 24c, 24d of the motor 6, and the pistons 28a, 28b, 28c, 28d are pressed against the eccentric cam 10b , and the main body 1 and the rotary shaft 9b Torque is transmitted during this time, and the rotating shaft 9b rotates.
[0040]
As shown in FIG. 3, the auxiliary machinery H connected to the rotating shaft 9 b of the motor 6 rotates in proportion to the rotational speed of the engine E.
[0041]
When the rotation of the engine E becomes a high speed rotation and the rotation speed of the pump 5 increases, the discharge amount per one stroke of the pump 5 decreases due to an increase in resistance due to the throttle passage 17 on the suction side of the pump 5, and FIG. As shown in a), the discharge amount Q of the pump 5 becomes constant regardless of the rotational speed Np of the pump 5 when the suction limit point L is exceeded at the rotational speed Nl.
[0042]
For this reason, the motor 6 is connected to the pump 5 and only has a rotational speed corresponding to the discharge amount Q of the pump 5, and the pump 5 reaches a certain rotational speed or more as shown in FIG. Then, the discharge amount Q of the pump 5 exceeds the suction limit point L and becomes constant, and the rotational speed Nm of the motor 6 becomes constant regardless of the rotational speed Np of the pump, and is compensated for at one end of the motor 6. The machine H does not have a rotation speed exceeding a certain level.
[0043]
Therefore, even if the rotation of the engine E becomes a high speed rotation, the auxiliary machinery H is driven at a rotation proportional to the rotation of the engine, but the rotation speed does not reach a certain level, and an excessive output is necessary. Can be used for energy saving without losing unnecessary energy in a high-speed rotation range.
[0044]
In addition, even if the auxiliary machines H have a wide engine speed of about 600 to 7000 rpm, the auxiliary machines H can be sealed, bearings, This eliminates the need for a high-speed rotation specification because it does not require a structure that takes pressure resistance into consideration, thereby significantly reducing the price and reducing costs.
[0045]
Furthermore, by changing the aperture of the throttle passage 17 that restricts the suction of the pump 5, it is possible to limit the discharge amount Q of the pump 5 and change the high-speed rotation speed region of the motor 6 at low cost.
[0046]
The radial piston pump 5 / motor 6 is sucked into the diameter expansion chambers 24a, 24b, 24c, 24d as the pistons 28a, 28b, 28c, 28d move in conjunction with the eccentric cams 10a, 10b. Passages 26a, 26b, 26c for communicating the discharged hydraulic oil with the enlarged diameter chambers 24a, 24b, 24c, 24d at the pistons 28a, 28b, 28c, 28d having a phase lag of 90 ° with the pistons 28a, 28b, 28c, 28d. , 26d are discharged from the pistons 28a, 28b, 28c, 28d having a phase delay of 90 ° so as to communicate with the discharge ports 15a, 15b, 15c, 15d or the suction ports 14a, 14b, 14c, 14d. Switching valve for switching between ports 15a, 15b, 15c and 15d or suction ports 14a, 14b, 14c and 14d Since it is configured so as to serve as well, the hydraulic fluid that is sucked and discharged as the pistons 28a, 28b, 28c, and 28d move is drawn into the suction ports 14a, 14b, 14c, and 14d and the discharge ports 15a, 15b, 15c, and 15d. Therefore, the piston 28a, 28b, 28c, 28d is in direct contact with the eccentric cams 10a, 10b and directly driven with a phase difference in each axial direction. The opening degree of the spool following the piston speed at the high speed rotation of the rotating shaft can be obtained, and even in the discharge stroke, there is little pressure loss and the volumetric efficiency can be improved.
[0047]
【The invention's effect】
According to the first invention, the body , the plate fastened to the body via the seal member, the rotating shaft that is rotatably supported through the plate, and the rotating shaft are coupled. An eccentric cam interposed in a cam chamber formed in the body, a piston interlocking with the eccentric cam, a cylinder radially formed around a rotation shaft in a body into which the piston is slidably inserted, A diameter expansion chamber formed at the other end, and a radial piston pump and motor configured to supply and discharge hydraulic oil in the expansion chamber by piston operation, the radial piston pump and motor being connected via a cam chamber, the radial piston pump and motor - by regulating the suction of communicating via a passage aperture for the cam chamber of data the radial piston pump motor - so as to limit the rotational speed of the motor So the engine Even if the rotation of the motor becomes high-speed, the auxiliary machines H are driven at a rotation proportional to the rotation of the engine, but the motor rotation does not reach a certain number of rotations and is excessively larger than necessary. Therefore, it is possible to save energy without losing unnecessary energy in a high-speed rotation range. Further, even if the auxiliary machine H has a wide engine speed of about 600 to 7000 rpm, the auxiliary machine H can be sealed, bearing, This eliminates the need for a structure that takes pressure resistance into consideration, thereby eliminating the need to comply with high-speed rotation specifications, significantly reducing costs, and reducing costs. In addition, the diameter of the throttle passage can be reduced by simply processing with a drill or the like, and the pump suction can be restricted by changing the aperture to change the high speed rotation speed of the motor.
[0049]
According to the second aspect of the present invention, the radial piston pump motor has a phase delay of 90 ° with respect to the piston by sucking and discharging the working oil sucked into the diameter expansion chamber as the piston moves in conjunction with the eccentric cam. A switching valve that switches the discharge port or the suction port at each piston with a phase delay of 90 ° so that the passage communicating with the expansion chamber at a certain piston communicates with the discharge port or the suction port. Since it is configured so that it also serves as a piston, there is no need for a switching valve that switches between the suction port and the discharge port for the hydraulic oil that is sucked and discharged as the piston moves, and the configuration is simple and the cost can be reduced. Since it is slidably contacted with the eccentric cam and directly driven with a phase difference in each axial direction, the opening degree of the spool following the piston speed at the high speed rotation of the rotating shaft can be obtained. Less loss, It is possible to improve the product efficiency.
[Brief description of the drawings]
FIG. 1 is a longitudinal sectional view of a rotation speed limiting device showing an embodiment of the present invention.
FIG. 2 is a longitudinal sectional view of an essential part of the radial piston pump motor.
FIG. 3 is a hydraulic circuit diagram of the rotation speed limiting device.
FIG. 4A is a view showing the relationship between the discharge amount Q of the radial piston pump and the rotational speed Np.
(B) It is a figure which similarly shows the relationship between the rotational speed Np of a radial piston pump, and the rotational speed Nm of a motor.
[Explanation of symbols]
1 Body 2 Body 3a, 3b Plate 4 Angle 5 Pump 6 Motor 7a, 7b Bearing 7c, 7d Needle bearing 8a, 8b Seal member 9a, 9b Rotating shaft 10a, 10b Eccentric cam 10c, 10d Eccentric Cam outer periphery 11a, 11b Bearing 11c, 11d Bearing outer periphery 12a, 12b Cam chamber 13a, 13b, 13c, 13d Cylinder 14a, 14b, 14c, 14d Suction (discharge) port 15a, 15b, 15c, 15d Discharge (supply) port -To 16 passage 17 throttle passage 18 bolt 19 bolt 20 seal member 21a, 21b, 21c, 21d expanded diameter portion 22 seal member 23a, 23b, 23c, 23d plug 24a, 24b, 24c, 24d expanded diameter chamber 25a , 25b, 25c, 25d ports 26a, 26b, 26c, 26d passage 27a, 7b, 27c, 27d Annular grooves 28a, 28b, 28c, 28d Pistons 29a, 29b, 29c, 29d Step diameter part 30 Spring E Engine H Auxiliary equipment L Suction limit point Np Pump speed Nm Motor speed Q Pump discharge amount

Claims (2)

A body, a plate fastened to the body via a seal member, a rotating shaft that is rotatably supported through the plate, and a cam chamber that is coupled to the rotating shaft and formed in the body. Interposed eccentric cam, piston interlocking with the eccentric cam, cylinder formed radially around the rotation shaft in the body into which the piston is slidably inserted, and diameter expansion formed at the other end of the cylinder A chamber, a radial piston pump configured to supply and discharge hydraulic oil in the expansion chamber by piston operation, and a motor,
Connecting the radial piston pump and the motor via the cam chamber;
It said radial piston pump and motor - motor by regulating the communicating suction of said radial piston pump via a throttle passage of the cam chamber of the motor - rotary speed limiting device and limits the rotational speed of the motor.   The radial piston pump and the motor include a diameter-expanded portion formed on the other end side of the cylinder, a plug having a step-diameter portion that is hermetically sealed and inserted into the diameter-expanded portion by a seal member, and the plug. A diameter expansion chamber partitioned by the diameter expansion portion, a passage communicating with the cylinder having a phase difference of 90 ° radially around the rotation axis from the diameter expansion chamber, and a phase delay of 90 ° from this passage A piston having an annular groove to be inserted and inserted to cut off the communication between the suction port and the discharge port provided in the cylinder having the difference between them, and urging one end of the piston to slidably contact the outer periphery of the eccentric cam A spring mounted on the step diameter portion of the plug, and while the expansion chamber is enlarged by a piston interlocking with an eccentric cam every rotation of the rotary shaft, the passage is delayed by a phase of 90 °. Communicate with the suction port of the cylinder with the difference, 2. The rotation speed limiting device according to claim 1, wherein the passage is configured to communicate with a discharge port of a cylinder having a phase difference of 90 degrees while the diameter chamber is reduced. .

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