JPS58148282A - Liquid pressure generating device - Google Patents

Abstract

PURPOSE:To simplify the construction of a fuel control system by regulating the transient time from the expansion to compression stroke, making possible the output control without changing the combustion condition and by eliminating necessity for making variable the amount of fuel injection per cycle. CONSTITUTION:When a liquid pressure piston 204 moves outward, the capacity of the rod side cylinder chamber 203b increases, so that the working liquid in the low-pressure side accumulator 21 flows through a check valve 218 into the cylinder chamber 203b. When thus the expansion stroke is finished and the liquid pressure piston 204 stops at the outer dead point a, the working liquid in the high-pressure side accumulator 209 is again supplied to the cylinder chamber 203a through a throttle valve 226, and the device continues to operate. The opening of throttle valve 226 can be changed by control signal S2 to give a change the number of cycles per unit time. Thus the output can be regulated. Accordingly it is not required to make variable the amount of fuel injection per cycle, so that the construction of the fuel control system can be simplified.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a pressurized fluid generating device which is configured to convert the energy of combustion gas in an internal combustion cylinder into hydraulic energy through the reciprocating motion of a free piston to generate pressurized fluid. It is something.

Conventionally, in this type of pressure fluid generator, output energy that immediately responds to the magnitude of hydraulic energy load 1, for example, the magnitude of hydraulic energy consumed by a hydraulic motor connected to the output side, is generated by a two-stroke internal combustion cylinder. It is common to generate this by adjusting the combustion layer within the combustion chamber. However, in this type of system, the fuel supply tray per cycle must be changed depending on the size of the load, so the structure of the fuel control system becomes complicated.
During partial loads where the amount of energy consumed is relatively small, such as during hydraulic pressure Tanabata, the engine is operated with a low average gas pressure in the internal combustion cylinder, making it impossible to maintain high thermal efficiency. Furthermore, since the combustion conditions within the internal combustion cylinder change due to load fluctuations, it is difficult to design the combustion chamber and take measures against exhaust gas.

The present invention was made with attention to such circumstances, and
Explosion instead of changing the combustion conditions in the internal combustion cylinder,
To provide a pressurized fluid generating device capable of eliminating the above-mentioned disadvantages by controlling the opening time of transition from the expansion step to the compression step sv for each cycle and adjusting the output. It is.

Hereinafter, embodiments of the present invention will be described with reference to Figure Eii.

Embodiment 1 (Fig. 111) A free piston 102 is fitted in a two-stroke internal combustion cylinder 101, which has an intelligent configuration, so as to be able to reciprocate. Further, a hydraulic cylinder 108 is disposed near the internal combustion cylinder 101, and a hydraulic piston 104 is fitted into the hydraulic cylinder 108. Then, this hydraulic piston 104 is connected to the free piston 10 via a rod 105.
2, the hydraulic piston 104 is interlocked with the free piston 102 and reciprocated between the outer dead center a and the inner dead center. Also,
The main port 106 is opened at a portion of the inner periphery of the hydraulic cylinder 108 that is located slightly inward of the outer dead center island of the hydraulic piston 104, and further than the outer dead center a of the hydraulic cylinder 101. The auxiliary boat 107 is opened at a portion of the outer cover, for example, a portion of the end cover. Seventh, the main port 106 and the auxiliary boat 10
A pressure fluid derivation line 108 for output is connected to the main port 106Iζ and a hydraulic fluid supply line 109 for compression.
Further, a hydraulic fluid supply line 111 for cycle control is connected to the auxiliary boat 107. To be more specific, the pressure liquid derivation system 108 connects the main pipe 112, which has one end connected to the main boat 106Ir, and the main pipe 112, which connects the auxiliary boat 107 to the main pipe 112 through the check valve 11g. A branch pipe 114 for deriving pressure fluid and the other end of the main pipe 112 are connected to an inlet 1171 of a hydraulic motor 117 as a load via a check valve 116 and a high-pressure side accumulator 116. It has a pipe line 118 for communicating with the pressure liquid output. - The hydraulic fluid supply line 109 for 10,000 compressions connects the outlet 117k of the hydraulic motor 117 to the main pipe line 112 via the low pressure side accumulator 119 and the check valve 121.
It is composed of pipes 1 and 2 for recovering hydraulic fluid and a main casting pipe 112 that communicates with the hydraulic fluid recovery pipes 1 and 2. The cycle control hydraulic fluid supply system 111 includes a hydraulic fluid supply branch pipe 121B that branches from the middle of the main pipe 112 and reaches the auxiliary boat 107. A throttle valve 124 whose opening degree can be adjusted is inserted in the middle of 1211.

Note that 126 is a leak supply pump, 126 is a starting pump, and 127 is a starting opening/closing valve.

Next, the operation of this embodiment 1+this device will be explained.

The low pressure side accumulator 1 is removed by the leakage replenishment pump 125.
19 is accumulated in advance, and the starting on-off valve 127 is closed by the control signal 81, and the starting pump 126 is activated.
From hydraulic cylinder 1080 rod double cylinder chamber TOSB
Supply hydraulic fluid to. Then, the hydraulic piston 1
04 moves to external dead center a.

Next, the starting on-off valve 127 is controlled by the signal 8. The cylinder chamber 108b is then closed and the rod cylinder chamber 108b is opened to the tank. As a result, the pressure in the rod pair cylinder chamber 108b decreases, so that the hydraulic fluid in the low pressure side spacer and mulrator 119 is guided to the auxiliary boat 107 of the hydraulic cylinder 108 through the check valve 121 and the throttle valve 124. , from this auxiliary boat 107 to the end cover side cylinder chamber 108a.
flows into. In response, the piston 104 moves inward (to the left in the figure) at a slow speed. In this way, the hydraulic piston 104 slowly moves inward from the external dead center a, and the main #-) 10 of the hydraulic cylinder 108, which had been closed by the piston 1041U,
6 opens, the working fluid from the low pressure side accumulator 119 introduced into the main pipe line 12 through the check valve 121 is directly supplied to the end cutter side silling chamber 1081 through the main boat 106. Therefore, the hydraulic piston 104 moves all at once to the circle dead center brc, and the gas in the internal combustion cylinder 101 is compressed. When the compression stroke ends in this way and the gas in the internal combustion cylinder 101 yen expands, the hydraulic cylinder 1
The hydraulic fluid in the cylinder chamber 108a that is removed by G4 flows out into the main pipe line 111 through the main port 108, and is sent to the high pressure side achievator 116 via the check valve 116. After the hydraulic piston 104 closes the main port 106, the hydraulic fluid in the cylinder chamber 108a is transferred to the auxiliary port 1.
07 and the check valve 118 to the main pipe line 112, and also flows through the check valve 116 to the high pressure side accumulator 1.
Sent to 16. And this high pressure side accumulator 1
The high-pressure hydraulic fluid stored in the hydraulic motor 16 is sequentially supplied to the hydraulic motor 117 as an output pressure fluid. In this manner, when the expansion stroke is completed and the hydraulic piston 104 stops at the outer dead center island, both the check valves 118 and 115 are automatically closed, and the hydraulic fluid in the low pressure side accumulator 119 is passes the check valve 11i1 and the throttle valve 124. When the hydraulic piston 104 begins to move circularly at low speed from the outer dead center a, and the hydraulic piston 104 moves to a position where the main port 106 is closed. The compression stroke begins as described above. At this time, the time required for the hydraulic piston 104 to move from the outer dead center island to the position where the main port 106 is opened will be longer if the throttle valve 124 is opened smaller, and shorter if the opening is larger. Therefore, by changing the opening degree of the throttle valve 124 using the control signal 8., the number of cycles per unit time can be changed, and the output can be adjusted.The control signal 8. , a mechanical signal, or an electrical signal, the output value of which depends on the pressure within the high overwhelm accumulator 116, the position of the outer dead center island of the hydraulic piston 104, the gas pressure within the internal combustion cylinder 101, etc. It is to be determined.

Embodiment 2C1142) The device of this embodiment includes an internal combustion cylinder 2G1, a free piston 202. [pressure shilling 2
08, hydraulic piston 204, rod 205, main port 2
06 and an auxiliary port 207.

The pressure liquid lead-out line 20g of this embodiment 2 includes a main pipe line 211 that communicates the main port 20g with the high pressure side space and the mulleter 209, and an auxiliary 1-) 2G? A branch passageway 218 for deriving pressure fluid that communicates with the middle of the main pipeline 211 via a check valve 214, and a pressure fluid that communicates the high pressure side Akiemulator 209 with the inlet port 214 & of the hydraulic motor 214 as a load. It has a pipe line 215 for liquid output. Further, a hydraulic fluid supply line 216 for compression communicates a hydraulic fluid outlet 214b of the hydraulic motor 214 with the rod side cylinder chamber 208b of the hydraulic cylinder 20B via a low pressure side achievator 217 and a check valve 218. Conduit 219 for
, a pipe line 222 for replenishing the hydraulic fluid that moves the cylinder chamber 2osb to the high-pressure side accumulator 2091ζ via the check valve 221, and the high-pressure side accumulator 20
9 to the main port 206
It is equipped with. Further, the cycle control hydraulic fluid supply line 224 is a hydraulic fluid supply branch line 22 that branches from the middle of the main line 211 and reaches the forward motion auxiliary port 207Iζ.
5, and a throttle valve 226 whose opening degree can be adjusted is inserted in the middle of this branch pipe line 226. In addition, 227
22B is a starting on-off valve, and 229 is a starting pump.

Next, the operation of this device in Example 21 will be explained.

First, the leak replenishment pump 227 and the starting pump 229 are operated to accumulate pressure in both accumulators 209 and 217 to a predetermined pressure. Then, the starting on-off valve 228 is switched in response to the control signal 8Siζ, and the main port 206 is opened to the tank. As a result, the U hydraulic piston 204 moves to the outer dead center island. Next K.

Return the starting on-off valve 228 to the original position shown in the figure.

As a result, the high pressure side accumulator 2. ．． The hydraulic fluid in 09 passes through the throttle valve 226 and is led to the auxiliary port 207 of the hydraulic cylinder 208, and flows from the auxiliary port 207 into the end cover side cylinder chamber 208&.

1 [In response, the piston 204 moves inward (leftward in the figure) at a slow speed. Then, when the piston 204 moves to the position where the main port 206 is opened, the high pressure side accumulator 209 The hydraulic fluid is directly supplied into the cylinder chamber 20g on the end cover side through the main port 206. Therefore, the hydraulic piston 204 moves all at once to the internal dead center, and the gas in the internal combustion cylinder 201 is compressed. Note that when the hydraulic piston 204 moves inward, the hydraulic fluid in the rod cylinder chamber 208b is sent to the high-pressure side Akiemulator!!09 through the check valve 221. Both cylinder chambers 208 and 20ab of the cylinder 208 are filled with high-pressure hydraulic fluid.
Since there is a pressure receiving area difference corresponding to the cross-sectional area of , an inward urging force continues to act on the hydraulic biston 204 due to the difference. In this way, the compression process is completed,
When the gas in the internal combustion cylinder 201 moves to the expansion stroke, the hydraulic fluid in the cylinder chamber 2081, which is removed by the hydraulic cylinder 204, flows out to the main pipe line 211 through the main port 206 and is sent to the high pressure side accumulator 209. It will be done. After the hydraulic piston 204 closes the main port 206, the hydraulic fluid in the cylinder chamber 208 flows out into the main line 211 through the auxiliary port 207 and the check valve 212, and is also sent to the high pressure side accumulator 209. The high-pressure hydraulic fluid stored in this high-pressure side accumulator 209I is sequentially transferred to the hydraulic motor 21 as an output pressure fluid.
4. Note that when the hydraulic piston 204 moves outward, Cζ increases the volume of the rod-side cylinder chamber 208b, so the hydraulic fluid stored in the low-pressure side accumulator 217 passes through the back pressure valve 218 and flows into the cylinder chamber 20.
8b inflow. In this way, when the expansion stroke is completed and the hydraulic piston 204 stops at the external dead center a, the hydraulic fluid in the high pressure side accumulator 209 flows to the throttle valve 2 again.
26 and into the cylinder chamber 208&,
The device will continue to operate as in Example 1 above. Also in this embodiment 2I, by changing the opening degree of the penalty throttle valve 226 using the control signal 8, the number of cycles per unit time can be changed, and the output can be adjusted. can.

Example $ (Figure 3) Internal combustion cylinder 801 yen and free piston so forming a pair
w and son are fitted together so that they can reciprocate.

Further, a hydraulic cylinder 1 is provided near the internal combustion cylinder 801.
04 are arranged in parallel, and a pair of hydraulic pistons 806.80@ are accommodated in this hydraulic cylinder 804 (,N).

Then, one 7-two piston 802 and one hydraulic piston 306 are connected via the first pressure increasing rocking arm A 807, and the other free piston 8011 and the other hydraulic piston 80@ are connected to each other via the IK. They are connected via a spirit pressure increasing swing arm 808. Each swinging arm 807.
808 uses the hydraulic cylinder leaning part in the middle as the fulcrum!
$09.811 is a see-saw type that is pivoted and converts the reciprocating movement of each of the free pistons 802 and 808 into a column with a short stroke and a large force, and transmits the liquid pistons 806 and 808. I am told to do so. Also, the rack gear 81 from the opposite side of the hydraulic piston 806 and log! , 8111 are provided in an irregularly protruding manner, and a pinion gear 814, which is rotatably mounted in the center of the hydraulic cylinder 806, is engaged with both rack gears 812,818.
06, and thus both free pistons 802.808
I am trying to make them move synchronously. That is, in this device, both the free pistons 802, 808 move toward and away from each other at the same speed, and each of the hydraulic pistons 805.
806 is a symmetrical position External dead center a
It is designed to perform reciprocating motion between and inner dead center.

In addition, the main port 815 is opened at the part 1r located on the inner circumference of the hydraulic cylinder 30◆ than the outer dead center a (in the circular direction in terms of operation), and the main port 815 is opened from the outer dead center island Also, an auxiliary port 816 is opened at a portion located outside Tj-. Both ports 815 and 816I are connected to the same hydraulic pressure circuit as in the first embodiment. Therefore, the same parts will be given the same symbols and the explanation will be omitted here.

Embodiment 8I The operation of such a device also depends on the free piston 802.80B and the hydraulic piston 80, which form a pair.
5.806 is completely the same as that of the first embodiment except that it performs bilaterally symmetrical reciprocating motion. In addition, in this embodiment 8, both the hydraulic pistons! 106.806
The cylinder chamber 8041 formed in g1l corresponds to the end cover side cylinder chamber 108a in the first embodiment, and the cylinder chambers 804b, 804b formed on both sides of the hydraulic cylinder 804 correspond to the cylinder chamber 108a in the first embodiment. This corresponds to the rod side cylinder chamber 108bvc in .

In addition, in each embodiment 1.2.8 of the Tsubagi, the case where the flow rate of the hydraulic fluid supplied to the auxiliary I-toe is controlled by the throttle valve was explained, but for example, the same could be done by using an on-off valve instead of the throttle valve. It is also possible to perform various functions.

As explained above, in the present invention, by controlling the flow rate of the auxiliary port supply operation, the time required for transition from the expansion stroke to the compression stroke can be reduced to 1lffi. It becomes possible to control the output without changing the combustion conditions within the internal combustion cylinder. Therefore, with such a device, the amount of fuel injected per cycle can be made variable, and
The average gas pressure inside the internal combustion cylinder does not decrease even during partial loads when the amount of output energy is small, so high thermal efficiency can be maintained.Furthermore, the combustion conditions inside the internal combustion cylinder are Since there is no change, effects such as combustion chamber design and exhaust gas countermeasures can be obtained. Further, according to the configuration of the present invention, for example, compared to the case 8 in which the supply timing and flow rate of the compression hydraulic fluid are directly controlled, it is possible to adjust the output using a flow control device with a much smaller capacity. As shown in FIG. 14, control responsiveness and accuracy can be improved.

In addition, if the wave pressure enclosure including the hydraulic fluid supply system line and the pressure liquid lead-out system line is made as shown in Embodiment 2, and the hydraulic fluid for compression can be supplied from the high pressure side accumulator to the hydraulic cylinder, it is possible to Lower the pressure in the side accumulator
It becomes possible to rub it. Therefore, it is important to be able to increase the effective pressure difference of a hydraulic motor, etc. depending on the load, and to make the hydraulic motor, etc. smaller and lighter.

Furthermore, as in Example 8, 6ζ, opposed piston type i
ζ has the effect of speeding up the elimination of vibrations due to the inertia of the free piston.

[Brief explanation of drawings]

Section 11.1 is a circuit description showing one embodiment of the present invention.
1m is a circuit explanatory diagram showing another embodiment of the present invention, and FIG. 8 is a circuit explanatory diagram showing still another embodiment of the present invention. 101%! ! 01.801-・Internal combustion cylinder 10t,
20 teeth 8OL 80$-79-piston lO busy go&
go+-11 pressure cylinder 104.204.80FD%
5os-IF+pressure piston IH% 106.816-・
Main boat 107.207,816... Auxiliary 4-toe 1G & 20
8- Pressure liquid derivation line 109, 21m, ・Compression hydraulic fluid supply line 111.2
24... Cycle control hydraulic fluid supply system agent Patent attorney Hiroshi Akazawa Figure 1 Figure 2 Figure 3

Claims (1)

[Scope of Claims] A two-stroke internal combustion cylinder, a free piston provided within the internal combustion cylinder so as to be able to reciprocate, and a reciprocating piston connected to the free piston that reciprocates between the circular dead center on the connected side and the external dead center on the other side. A hydraulic piston that performs an operation, and an auxiliary I-port which slidably encloses the hydraulic piston and moves the main key to an outward position closer to the dead center than the external dead center of the hydraulic piston. When the hydraulic cylinder is opened and the hydraulic piston is located outward from the main port, a hydraulic fluid with a controlled flow rate is supplied from the auxiliary boat into the hydraulic cylinder.
A cycle control operation/liquid supply line for moving the hydraulic piston inward at a required speed; a compression hydraulic fluid supply line that supplies hydraulic fluid into the cylinder to move the hydraulic piston all at once to the circular dead center; and a compression hydraulic fluid supply system that supplies hydraulic fluid into the cylinder to move the hydraulic piston all the way to the dead center; The hydraulic cylinder is characterized by comprising a pressure fluid derivation system for leading out the hydraulic fluid in the hydraulic cylinder to the outside as pressure fluid for output when the hydraulic cylinder shifts from the inner dead center to the outer dead center. Pressure fluid generator.