WO1996024765A1 - Machine a piston a deplacement variable servant a limiter le bruit et les vibrations par diminution des pulsations du liquide d'evacuation - Google Patents

Machine a piston a deplacement variable servant a limiter le bruit et les vibrations par diminution des pulsations du liquide d'evacuation Download PDF

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Publication number
WO1996024765A1
WO1996024765A1 PCT/JP1996/000238 JP9600238W WO9624765A1 WO 1996024765 A1 WO1996024765 A1 WO 1996024765A1 JP 9600238 W JP9600238 W JP 9600238W WO 9624765 A1 WO9624765 A1 WO 9624765A1
Authority
WO
WIPO (PCT)
Prior art keywords
intermittent drain
cylinder
port
variable displacement
intermittent
Prior art date
Application number
PCT/JP1996/000238
Other languages
English (en)
Japanese (ja)
Inventor
Takashi Ochiai
Yasuyuki Murakami
Original Assignee
Daikin Industries, Ltd.
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from JP25745695A external-priority patent/JP3362576B2/ja
Application filed by Daikin Industries, Ltd. filed Critical Daikin Industries, Ltd.
Priority to KR1019960705689A priority Critical patent/KR100253947B1/ko
Priority to US08/722,132 priority patent/US5807080A/en
Priority to EP96901543A priority patent/EP0756084A4/fr
Publication of WO1996024765A1 publication Critical patent/WO1996024765A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F04B1/2014—Details or component parts
    • F04B1/2021—Details or component parts characterised by the contact area between cylinder barrel and valve plate

Definitions

  • the present invention relates to a variable displacement biston machine such as a variable displacement piston pump or a variable displacement piston motor.
  • variable displacement piston pump As shown in FIG. 15 (Japanese Utility Model Laid-Open No. 54-176102).
  • This variable displacement piston pump has a valve plate 53 provided with a suction port 51 as a low pressure port and a discharge port 52 as a high pressure port, and slides on the sliding surface of the valve plate 53. While rotating, the cylinder block 55 having a plurality of cylinders 54, 54 in the axial direction, and the swash plate 56 rotating the cylinder block 55, the cylinders 54, 5 4, a plurality of pistons 57, 57,. As shown in FIG.
  • a sliding surface 58 between the suction port 51 of the valve plate 53 and the discharge boat 52 has a bottom dead center indicated by B in the figure from the discharge port 52.
  • An oil guide groove 59 is provided extending toward the vicinity of.
  • the oil guide groove 59 includes a notch 59a and a V notch 59b, as shown in FIGS.
  • an object of the present invention is to provide a variable displacement piston machine having an oil guide groove for intermittently communicating a high pressure port and a cylinder, when a backflow does not occur in the oil guide groove, the high pressure port is connected to the high pressure port.
  • a variable-capacity view type piston machine provides a valve plate having a low pressure port and a high pressure port opened on a sliding surface, and a piston reciprocating in a plurality of cylinders provided in an axial direction.
  • a cylinder port communicating with the cylinder is opened on a sliding surface that slides on a sliding surface of the valve plate, and a cylinder block that reclaims the valve plate; and a low-pressure port of the valve plate.
  • An oil guide groove provided on a sliding surface between the high pressure port and the high pressure port, and extending from the high pressure port toward the dead center. The high pressure port and the cylinder port communicate with each other via the oil guide groove.
  • An intermittent drain passage is provided on the sliding surface of the valve blade, the intermittent drain passage being provided so as not to directly communicate with the high pressure port and the oil guide groove.
  • the variable displacement piston pump is a variable displacement piston pump.
  • the oil guide groove is provided on the sliding surface so as to extend from the high-pressure port toward the bottom dead center.
  • the bottom dead center is set before the cylinder port communicates with the high-pressure port. In the vicinity, it first communicates with the oil guide groove.
  • hydraulic oil gradually flows back from the high pressure port to the cylinder through the oil guide groove. Therefore, when the cylinder shifts from the low pressure port to the high pressure port, rapid pressure fluctuations in the cylinder and the high pressure port are prevented.
  • the intermittent drain passage does not communicate with the cylinder port, and therefore does not communicate with the high pressure port and the oil guide groove. Therefore, at this time, the hydraulic oil is not substantially flowing through the intermittent drain passage.
  • the intermittent drain passage is closed when there is a backflow in the oil guide groove, while the intermittent drain passage is opened when the backflow in the oil guide groove stops, and the hydraulic oil is discharged from the high pressure port to the drain. Therefore, pressure fluctuation in the high pressure port is reduced. Therefore, the pulsation can be reduced, the S noise and vibration can be reduced, and the operating characteristics of the entire device can be improved.
  • the intermittent drain passage does not intermittently communicate with the cylinder port and does not always generate a drain flow, the volume efficiency is higher than when a passage that constantly generates a drain flow is provided.
  • variable displacement piston machine is a variable displacement piston motor
  • the oil guide groove is provided on the sliding surface so as to extend from the high pressure port toward the top dead center, and the intermittent drain passage is connected to the high pressure port and the oil guide. It is provided near the groove. The operation is the same as that of the variable displacement piston pump.
  • the intermittent drain passage includes a first intermittent drain passage portion and a second intermittent drain passage portion.
  • the first intermittent drain passage communicates with the cylinder port and communicates with the high-pressure port via the cylinder port, and the second intermittent drain passage does not communicate with the cylinder port.
  • both the first intermittent drain passage and the second intermittent drain passage communicate with the cylinder port, and the high-pressure port is connected to the high-pressure port via the cylinder port.
  • the second intermittent drain passage In the third state, in which the cylinder block rotates from the second state, the second intermittent drain passage communicates with the cylinder port.
  • the high-pressure port communicates with the high-pressure port via the cylinder port, and the first intermittent drain passage does not communicate with the cylinder port.
  • the amount of backflow flowing through the oil guide groove is small t, and in the first state, the first intermittent drain passage communicates with the high pressure port via the cylinder boat, (2) The intermittent drain passage does not communicate with the cylinder port. Therefore, at this time, a small amount of hydraulic oil is discharged from the high pressure port to the drain only through the first intermittent drain passage.
  • both the first intermittent drain passage and the second intermittent passage communicate with the high-pressure port via the cylinder port. Therefore, at this time, a large amount of hydraulic oil is discharged from the high-pressure port to the drain through both the first intermittent drain passage and the second intermittent drain passage.
  • the second intermittent drain passage communicates with the high-pressure port via the cylinder port, while the first intermittent drain passage communicates with the high-pressure port.
  • the drain passage is not communicating with the cylinder port. Therefore, at this time, a small amount of hydraulic oil is discharged from the high pressure port to the drain only through the second intermittent drain passage.
  • the first and second intermittent drain passages control the flow rate of the drain in two stages according to the amount of backflow flowing in the oil guide groove, and determine the sum of the amount of backflow and the amount of drainage. Since it can be made substantially constant, pulsation in the high pressure port can be further reduced.
  • the intermittent drain passage is provided on the sliding surface of the valve plate, and is intermittently communicated with the cylinder port intermittently as the cylinder block rotates. Has a drain groove.
  • the intermittent drain passage formed in the intermittent drain passage is formed in the sliding surface.
  • the cylinder block slides against the sliding surface of the valve plate, and the valve plate receives small vibrations from the cylinder block.Therefore, the intermittent drain groove is clogged with dirt and foreign matter. It is difficult to remove, and even if it is clogged, dust is easily removed.
  • the first intermittent drain passage and the second intermittent drain passage are respectively provided with a first intermittent drain groove and a second intermittent drain provided on the sliding surface of the valve plate. It is a drain groove.
  • the valve plate receives small shocks and vibrations from the cylinder block, dirt and foreign matter are less likely to be clogged in the first and second intermittent drain grooves, and dust is easily removed even if clogged. .
  • the intermittent drain passage communicates with the intermittent drain groove provided on the sliding surface of the valve plate and the intermittent drain groove, and penetrates the valve plate in the axial direction. And a through hole communicating with the drain.
  • the intermittent drain groove on the above-mentioned sliding surface is hardly clogged with dust and the like because the cylinder block slides on it with a slight vibration. Even if clogged, it is easily removed. Furthermore, the hydraulic oil is discharged from the intermittent drain groove to the drain through a through hole that penetrates the valve plate in the axial direction, so that the flow direction of the hydraulic oil is changed at the connection point between the intermittent drain groove and the through hole, and the energy is reduced. As a result, noise when discharging hydraulic oil to the case drain and the like is reduced.
  • the intermittent drain passage is provided on a sliding surface of the valve plate, and is provided on a peripheral surface of the valve plate. It consists only of intermittent drain grooves that open.
  • the intermittent drain passage is constituted only by the intermittent drain groove opened on the peripheral surface of the valve plate, clogging due to dust and the like does not easily occur, and the dust and the like are easily removed.
  • the intermittent drain passage includes only a through hole penetrating the valve plate.
  • the intermittent drain passage has a plurality of intermittent drain grooves that sequentially communicate with the cylinder port as the cylinder block rotates.
  • the intermittent drain passage is composed of a plurality of intermittent drain grooves
  • the amount of hydraulic oil discharged to the drain through the intermittent drain passage is controlled in multiple stages according to the amount of backflow in the oil guide groove. be able to. Therefore, pulsation, vibration and noise can be further reduced.
  • the plurality of intermittent drain grooves are parallel to each other.
  • the intermittent drain passage extends through the valve plate in the axial direction and opens on the sliding surface and the back surface; and on the back surface of the valve plate. It is provided with the intermittent drain through hole and a groove communicating with the drain.
  • the diameter of the intermittent drain through hole can be increased, and the amount of intermittent drain can be regulated by the groove on the back surface.
  • the amount of the intermittent drain can be regulated by the groove on the back surface, so that the diameter of the intermittent drain through hole can be increased to prevent clogging.
  • the groove for regulating the amount of intermittent drain is provided on the back surface of the valve plate and not on the sliding surface, the dimensions do not change even if the sliding surface is worn. Therefore, according to this embodiment, the intermittent drain amount is not affected by the wear of the sliding surface of the valve plate.
  • the sliding surface of the valve plate is a part of a spherical surface
  • the back surface of the valve plate is a flat surface
  • the sliding surface of the cylinder block is the valve brake. This is a part of the spherical surface that fits on the sliding surface of the shaft.
  • the groove of the intermittent drain passage is provided on the back surface which is a plane of the valve plate, and the intermittent drain through hole of the intermittent drain passage is opened on the finger-acting surface which is a part of the spherical surface of the valve plate. . Therefore, it is not necessary to provide a groove for the intermittent drain passage on the sliding surface that is a part of the spherical surface, and therefore, the machining of the intermittent drain passage is facilitated.
  • the sliding surface of the valve plate and the sliding surface of the cylinder block are formed as spherical surfaces that fit each other, the area of the sliding surfaces that slide with each other increases, and the sliding surface between the sliding surfaces increases. As the leakage decreases and the surface pressure on the sliding surfaces decreases, their wear decreases.
  • the intermittent drain passage is formed of an intermittent drain groove provided on the sliding surface of the valve plate and having both ends closed. It is formed on the sliding surface of the cylinder block and always communicates with the annular groove communicating with the drain.
  • the intermittent drain is discharged from the intermittent drain groove of the sliding surface of the valve plate through the annular groove of the sliding surface of the cylindrical hook to the drain. Accordingly, the energy is gradually attenuated while the intermittent drain is discharged from the intermittent drain groove through the annular groove to the drain, so that noise is reduced.
  • the annular groove of the cylinder block is originally provided for balancing the pressure between the cylinder block and the valve plate, the intermittent drain passage is provided on the sliding surface of the valve plate. It is only necessary to form an intermittent drain groove with both ends closed. Therefore, the intermittent drain passage can be formed easily and inexpensively.
  • the intermittent drain groove extends in a substantially radial direction of the valve plate, and an outer end of the intermittent drain groove communicates with the annular groove.
  • the intermittent drain groove extends in the radial direction of the valve plate, it can be easily processed.
  • FIG. 1 is a front view of a valve plate of a variable displacement piston pump according to a first embodiment of the present invention.
  • 2A, 2B, and 2C are operation explanatory diagrams showing the positional relationship between the intermittent drain passage and the cylinder port shown in FIG.
  • 3A, 3B, and 3C are graphs showing the flow rate of the drain flowing through the intermittent drain passage and the amount of backflow flowing through the oil guide groove.
  • FIG. 4 is a graph showing the pulsation of the conventional example.
  • FIG. 5 is a graph showing the pulsation of the first embodiment.
  • FIGS. 6A, 6B and 6C are views showing the positional relationship between the intermittent drain passage and the cylinder port in the second embodiment.
  • FIGS. 7A, 7B and 7C are views showing the positional relationship between the intermittent drain passage and the cylinder port in the second embodiment.
  • FIG. 8A and 8B are diagrams showing the positional relationship between the intermittent drain passage and the cylinder port in the second embodiment.
  • FIG. 9 is a graph showing the drain flow rate flowing through the drain passage and the reverse flow rate flowing through the oil guide groove in the first embodiment.
  • FIG. 10 is a graph showing the drain flow rate flowing through the drain passage and the reverse flow rate flowing through the oil guide groove in the second embodiment.
  • FIGS. 11A, 11B, and 11C are a front view, a cross-sectional view, and a rear view of the valve plate of the third embodiment.
  • FIG. 12 is a front view of a valve plate according to a fourth embodiment.
  • FIG. 13 is a view showing the sliding surface of the cylinder block of the fourth embodiment.
  • FIG. 14 is a sectional view of a cylinder block according to the fourth embodiment.
  • FIG. 15 is a sectional view of a conventional variable displacement piston pump.
  • FIG. 16 is a front view of the valve blade of the variable displacement piston pump shown in FIG.
  • FIG. 17 is a cross-sectional view of the location of the oil guide groove of the valve plate shown in FIG. BEST MODE FOR CARRYING OUT THE INVENTION
  • FIG. 1 is a front view of a valve plate 1 of a variable displacement biston bomb according to a first embodiment of the present invention.
  • the components of the variable displacement piston pump other than the valve plate 1 are exactly the same as those of the conventional example shown in FIG. 15, and therefore, FIG. 15 is referred to for these components.
  • the valve plate 1 includes suction ports 2a, 2b, 2c as low pressure ports and discharge ports 3a, 3b, 3c as high pressure ports.
  • the suction ports 2a, 2b, 2c communicate with each other on the back side of the valve plate 1, and the discharge ports 3a, 3b, 3c are also not shown, but the valve plate is not shown. 1 on the back side Communicating.
  • the sliding surface 1 a of the valve plate 1 is provided with a V-shaped oil guide groove 4 of the shape extending to the vicinity of the bottom dead center B from the discharge port 3 a, from the suction port 2 c
  • a V-shaped oil guide groove 4 that extends to the vicinity of the top dead center T is provided.
  • the sliding surface 1a of the valve plate 1 is provided with an intermittent drain passage 5 located radially outward with respect to the root of the oil guide groove 4 extending from the discharge port 3a.
  • the intermittent drain passage 5 communicates with the intermittent drain groove 5 a extending in the radial direction, and communicates with the intermittent drain groove 5 a and penetrates the valve plate 1 in the axial direction to form a case drain 60 shown in FIG. 15. It consists of a communicating through hole 5b.
  • the intermittent drain passage 5 does not directly communicate with the oil guide groove 4 and the discharge port 3a. However, the intermittent drain passage 5 can be connected to the oil guide groove 4 and the discharge port 3a through the cylinder port 54a communicating with the cylinder 54 as follows.
  • the cylinder port 54a initially communicates with only the oil guide groove 4 near the top dead center B, When the block 55 rotates, it communicates with both the oil guide groove 4 and the intermittent drain passage 5 and the intermittent drain groove 5a. When the cylinder block 55 further rotates, the oil guide groove 4 and the intermittent drain groove 5 a and the discharge port 3a.
  • variable displacement piston pump having the above configuration operates as follows.
  • the cylinder block 55 rotates in the direction of the arrow while sliding on the valve plate 1, and as shown in Fig. 2A, the cylinder port 5 4a—1,5 4a — Suppose 2 is located.
  • Hydraulic oil at the flow rate is discharged to the intermittent drain groove 5a via 4a-1 and this hydraulic oil changes direction through the through hole 5b and is guided to the back side of the valve plate 1, Furthermore, it is discharged to the case drain 60. That is, in the state of FIG. 2A, the drain of the flow rate is discharged from the discharge port 3 a to the case drain 60 through the cylinder port 54 a-1 and the intermittent drain passage 5. This state is indicated by 1 in FIG. 3A.
  • next traveling cylinder port 54 a-2 near the bottom dead center overlaps and communicates with the oil guide groove 4.
  • the pressure in the cylinder 54 communicating with the cylinder port 54 a-2 has not yet sufficiently increased because only a small amount has passed since the start of the discharge stroke. Therefore, work dynamic oil discharge port Ichito 3 flow through the oil guide groove 4 from a cylinder port 5 4 a- 2 Q 2 gradually backflow. Therefore, the pressure in the cylinder 54 communicating with the cylinder port 54a-2 gradually increases. Therefore, when moving from the suction stroke to the discharge stroke, the pressure in the cylinder 54 does not rise sharply, and the pressure in the discharge port 3a does not drop sharply. Is reduced.
  • the above-mentioned intermittent drain passage 5 basically has an overlap with the cylinder port 54a when a backflow from the discharge port 3a to the cylinder port 54a through the oil guide groove 4 occurs.
  • the cylinder port 54a overlaps with the cylinder port 54a.
  • the hydraulic oil is discharged to the case drain 60 through the discharge port 3a.
  • FIG. 3 A, 3 B, and the backflow Q 2 from the discharge port 3 a into the cylinder 5 4, from the discharge port 3 a performs a drain ⁇ 3 1 to the intermittent drain passage 5 are alternately
  • the fluid Q 3 is discharged without change from the discharge port 3 a without fluctuation. Therefore, the pulsation on the discharge ports 3a, 3b, 3c side is reduced, vibration and noise are reduced, and the operation characteristics of the entire device are improved.
  • FIG. 5 shows the magnitude of the pressure pulsation (0.19 Pa) on the discharge ports 3 a, 3 b, and 3 c of the first embodiment. .1 9 Pa) It can be seen that the pulsation was reduced to 40% or less compared to the magnitude of the pulsation (0.5 Pa) of the conventional example shown in FIG.
  • variable displacement piston pump when a backflow is generated in the oil guide groove 4, the intermittent drain passage 5 is closed to stop draining. As a result, volumetric efficiency is improved.
  • the intermittent drain groove 5a is provided on the sliding surface 1a of the valve plate 1, so that the cylinder block 55 slides on the sliding surface 1a. Foreign matter such as dust is hardly clogged in the intermittent drain groove 5a due to small vibrations and the like, and even if clogged, it is easy to remove.
  • FIGS. 6A, 6B, 6C, 7A, 7B, 7C, 8A, 8B are diagrams illustrating the operation of the variable displacement piston pump according to the second embodiment of the present invention.
  • This variable displacement piston pump has nine cylinders 54 and cylinder ports 54a provided at equal intervals of 40 degrees in the cylinder block port 55 shown in Fig. 15, and an intermittent drain passage. Only the structure of 15 is different from that of the first embodiment. Components having the same configuration as the components of the first embodiment are denoted by the same reference numerals as those of the first embodiment, and description thereof will be omitted.
  • the sliding surface 11a of the valve plate 11 of the variable displacement piston pump of the second embodiment is provided independently of the discharge port 3a and the oil guide groove 4. (Separately), an intermittent drain passage 15 is provided.
  • This intermittent drain The passage 15 is provided with two parallel narrow first and second intermittent drain grooves 15 a and 15 b extending in the radial direction, and communicates with the first and second intermittent drain grooves 15 a.
  • a wide third intermittent drain groove 15 c extending to the end face of the valve plate 11.
  • the cylinder ports 54a are provided at regular intervals of 40 degrees, the cylinder ports 54a rotate the discharge port 3a, 3b, 3c, and the suction ports 2a, 2b, 2 when the cylinder block 55 rotates 40 degrees. The same positional relationship is repeated for c and the intermittent drain passage 15.
  • the tip of the oil guide groove 4 overlaps and communicates with the cylinder port 54a-2, and the preceding cylinder port 54a-1 is connected to the discharge port 3a and the 1.2 intermittent drain groove 15a. , 15b overlap and communicate. Therefore, at this time, the hydraulic oil in the high-pressure discharge port 3a gradually flows into the subsequent cylinder port 54a-2 and the cylinder 54 through the oil guide groove 4, and the pressure fluctuation in the cylinder 54 is moderated. At the same time, the fluid is discharged radially through the preceding cylinder port 54a-1, the first and second intermittent drain grooves 15a and 15b, and the third intermittent drain groove 15c, and is discharged to the case drain 60.
  • the sum of the amount of hydraulic oil flowing backward in the oil guide groove 4 and the amount of hydraulic oil discharged from the third intermittent drain groove 15c is substantially constant.
  • the cylinder port 54a-1 and the second intermittent drain groove 15b separate from each other, while the oil guide groove 4 and the subsequent cylinder The overlap with port 54a-2 increases. Therefore, there is no drain from the discharge port 3a to the drain passage 15.
  • the amount of backflow through the oil guide groove 4 increases. The amount of this backflow is substantially equal to the sum of the amount of hydraulic oil flowing backward in the oil guide groove 4 and the amount of hydraulic oil discharged from the third intermittent drain groove 15c shown in FIG. 6A.
  • the subsequent cylinder port 54a-2 greatly overlaps the oil guide groove 4 and the first intermittent drain groove. Communicate overlapping 15 a.
  • the pressure of the subsequent cylinder port 54a-2 and the cylinder 54 communicating therewith is higher than in the state shown in Fig. 6C, so that the discharge port 3a passes through the oil guide groove 4
  • the amount of backflow flowing into the subsequent cylinder port 5 4 a-2 is reduced.
  • the subsequent cylinder port 54a-2 since the subsequent cylinder port 54a-2 communicates with the first intermittent drain groove 15a, the amount of drain flow through the first intermittent drain groove 15a reduces the amount of backflow reduction. Will be added. Therefore, in FIG. 7A, the amount of hydraulic oil flowing from the discharge port 3a to the subsequent cylinder 54 and the first intermittent drain groove 15a is the amount of backflow in the oil guide groove 4 in the state shown in FIG. 6C. Is approximately equal to
  • the cylinder block 55 is rotated by 20 degrees.
  • the pressure in the subsequent cylinder port 54a-2 and the cylinder 54 communicating therewith rises and becomes substantially equal to the pressure in the discharge port 3a, and the hydraulic oil flows from the oil guide groove 4 to the cylinder 54. Stop flowing.
  • the following cylinder boat 54a-2 overlaps and communicates with both the first and second intermittent drain grooves 15a and 15b, it is discharged to the case drain 60 through the first and second intermittent drain grooves 15a and 15b.
  • the amount of hydraulic oil to be discharged is greater than the amount of hydraulic oil discharged to the case drain 60 through only the first intermittent drain groove 15a shown in FIG. 7A. As a result, in the state shown in FIG.
  • the amount of hydraulic oil discharged from the discharge port 3a to the case drain 60 via the cylinder ports 54a-2 and the first and second intermittent drain grooves 15a and 15b is as shown in FIG.
  • the amount is approximately equal to the amount of hydraulic oil flowing from the discharge port 3a to the subsequent cylinder 54 and the first intermittent drain groove 15a.
  • FIG. 7C shows a state in which the cylinder block 55 has been rotated 25 degrees
  • FIG. 8A shows a state in which the cylinder block 55 has been rotated 30 degrees
  • the pressure in the subsequent cylinder port 54a-2 and the cylinder 54 communicating therewith is substantially equal to the pressure in the discharge port 3a side.
  • the first and second intermittent drain grooves 15a and 15b communicate with the subsequent cylinder boat 54a-2, so the cylinder port 54a-2 from the discharge port 3a, the oil guide groove 4, and the first and second intermittent drains Hydraulic oil is discharged to the case drain 60 through the grooves 15a.15b and the third intermittent drain groove 15c.
  • This amount of hydraulic oil discharged is substantially equal to the amount of hydraulic oil discharged to the case drain 60 in FIG. 7B.
  • FIG. 8B shows a state in which the cylinder block 55 has rotated 35 degrees.
  • the subsequent cylinder port 54a-2 becomes Although not shown, while being separated from the first intermittent drain groove 15a, the second intermittent drain groove 15b, the oil guide groove 4, and the discharge port 3a overlap and communicate with each other. Therefore, since only the second intermittent drain groove communicates with the cylinder port 54a-2, the hydraulic oil discharged from the discharge port 3a to the case drain 60 through the second intermittent drain groove 15b and the third intermittent drain groove 15c. Is smaller than the amount of hydraulic oil discharged to case drain 60 in FIG. 8A.
  • the presence or absence and the size of the drain passing through the intermittent drain passage 15 are controlled in such a way that the fluid flows through the intermittent drain passage 15, so the amount of backflow through the oil guide groove 4 and the drain passing through the intermittent drain passage 15 The sum with the amount can be almost constant. Therefore, the pulsation at the discharge ports 3a, 3b, 3c can be reduced, noise and vibration can be reduced, and the operating characteristics of the entire device can be improved.
  • Fig. 10 shows an aspect in which the first and second intermittent drain grooves 15a and 15b of the second embodiment control the drain flow in two stages to compensate for the increase or decrease in the amount of backflow through the oil guide groove 4.
  • Q 2 represents the reverse flow rate through the oil guide groove 4.
  • Qu represents the drain flow rate by only one of the first and second intermittent drain grooves 15a and 15b.
  • Ch SxQu has a first intermittent drain groove 15a and a second intermittent drain groove 15b. Represents the drain flow rate.
  • the drain flow rate is controlled in two stages, the presence / absence and increase / decrease of the backflow of the oil guide groove 4 are compensated with higher accuracy than that of the first embodiment shown in FIG. Can be.
  • the intermittent drain passage 15 is closed so that the drain is not discharged. Volumetric efficiency is improved compared to the structure.
  • the intermittent drain passage 15 is formed only by the first, second, and third intermittent drain grooves 15a, 15b, and 15c in which the cylinder block 55 slides while performing minute vibration.
  • dust and the like are not easily clogged in the intermittent drain passage 15, and even if clogged, it is easily removed.
  • the intermittent drain passage 15 is composed of only the first, second, and third intermittent drain grooves 15a, 15b, and 15c, so that machining is easy. Further, since the first and second intermittent drain grooves 15a and 15b are parallel to each other, the working is easy.
  • a total of two first and second intermittent drain grooves 15a and 15b are opened and closed by the position of the cylinder port 54a with respect to the discharge port 3a. More than one intermittent drain groove may be opened and closed by the position of the cylinder boat with respect to the discharge port.
  • the intermittent drain passage may have no groove, and may include only one or a plurality of through holes penetrating the valve plate. In this case, processing becomes easy.
  • FIGS. 11A, 11B, and 11C show a third embodiment.
  • the same components as those in the first and second embodiments are denoted by the same reference numerals and description thereof will be omitted.
  • the sliding surface 7 la that is the surface of the valve plate 71 is formed of a part of a spherical surface, and the back surface 7 lb is formed of a flat surface.
  • the valve plate 71 has V-shaped discharge ports 3a, 3b, 3c, which are high pressure ports, and suction ports 2a, 2b.2c, which are low pressure ports.
  • Oil guide grooves 4 are provided, which have the same configuration as those of the first embodiment and perform the same functions.
  • a large-diameter intermittent drain through hole 75a is provided at a position radially outside the valve plate 4 with respect to the oil guide groove 4 near the bottom dead center B of the sliding surface 7la of the valve plate 71.
  • a radial groove 75b communicating with the opening of the intermittent drain through hole 75a is provided in the rear surface 7 lb of the valve plate 11.
  • the outer end of the radial groove 75b communicates with an annular groove 74 provided on the straight surface 7 lb, and the annular groove 74 communicates with a drain (not shown) by a notch 77.
  • the intermittent drain through hole 75a communicates with the drain through the radial groove 75b, the annular groove 74, and the notch 77.
  • the intermittent drain passage 75 is formed by the intermittent drain through hole 75a and the radial groove 75b.
  • the intermittent drain through hole 75a of the intermittent drain passage 75 is provided with the discharge port 3a and the discharge port 3a at the beginning when the discharge port 3a and the cylinder port (not shown) communicate with each other through the oil guide groove 4. It does not communicate with the oil groove 4 and the cylinder port, and when the cylinder block (not shown) rotates, it communicates with the discharge port 3a via the cylinder port.
  • the intermittent drain passage 75 When there is backflow to 4, the intermittent drain passage 75 is closed, while when there is no backflow to the oil guide groove 4, the intermittent drain passage 75 communicates with the discharge port 3a via the cylinder port to discharge from the discharge port 3a to the drain.
  • the hydraulic fluid is drained. Therefore, the pulsation in the discharge ports 3a, 3b, 3c is reduced, and the noise and vibration are reduced.
  • an annular stepped portion 76 is provided on the outer peripheral portion on the sliding surface 7 la side of the valve plate 71.
  • the diameter of the intermittent drain through hole 75a is increased, and the amount of the intermittent drain is regulated by the groove 75b on the back surface 71b.
  • the amount of intermittent drain is regulated by the groove 75b of the inner surface 71b, the diameter of the intermittent drain through hole 75a opening in the sliding surface 71a is increased, and the diameter of the intermittent drain through hole 75a is increased. Clogging can be prevented.
  • the groove 75b for regulating the amount of intermittent drain is located on the back surface 7lb of the valve plate 71 and not on the sliding surface 7la, the dimensions do not change even if the sliding surface 7la is worn. . Therefore, the amount of intermittent drain is not affected by the wear of the sliding surface # 1a of the valve plate 71.
  • the groove 75 b of the intermittent drain passage 75 is provided on the back surface 7 lb which is a plane of the valve plate 71, and the sliding surface 7 la which is a part of the spherical surface of the valve plate 71 has the intermittent drain passage 75 b.
  • 75 intermittent drain through hole 75a is open. Accordingly, it is not necessary to provide the groove 75b for adjusting the intermittent drain amount of the intermittent drain passage 75 on the sliding surface 7la which is a part of the spherical surface, and the intermittent drain passage 75 can be easily processed.
  • the sliding surface 7 la of the valve plate 71 and the sliding surface of the cylinder block are formed as spherical surfaces that abut each other, the area of the sliding surfaces that slide with each other increases, and the sliding surface between the sliding surfaces increases. And the wear on the sliding surfaces is small due to the low surface pressure of the sliding surfaces.
  • FIGS. 12, 13, and 14 show a fourth embodiment.
  • the valve plate 81 is provided with discharge ports 3a.3b, 3c, suction ports 2a, 2b, 2c, and a V-shaped oil guide groove 4.
  • the intermittent drain groove 8 with both ends closed and extending in the radial direction at a location radially outside the valve plate 4 with respect to the oil guide groove 4 near the bottom dead center B of the sliding surface 8 la of the valve plate 8 1 8 5 are provided.
  • This intermittent drain groove 85 alone forms an intermittent drain passage 85.
  • the communication relationship between the intermittent drain groove 85 and the cylinder port 94a (see FIGS. 12 and 14) and the oil guide groove 4 is the same as in the first embodiment.
  • a cylinder port 94 a is provided on the same circumference.
  • a plurality of openings are provided at intervals.
  • an annular groove 97 located outside the cylinder ports 94 a, 94 a,... Is provided on the sliding surface 95 a of the cylinder hook 95. .
  • the annular groove 97 communicates with the outer end of the intermittent drain groove 85 formed on the sliding surface 8la of the cylinder block 81.
  • the annular groove 97 communicates with the drain through cutouts 98a, 98b, 98c provided at intervals of 120 degrees on the circumference.
  • the intermittent drain is formed from the intermittent drain groove 85 of the sliding surface 8 la of the valve plate 81 to the annular groove 97 of the sliding surface 95 a of the cylinder block 95. Drained through notches 98a, 98b, 98c. Accordingly, while the intermittent drain is discharged from the intermittent drain groove 85 to the drain through the annular groove 97, the energy is gradually attenuated, so that noise is reduced.
  • the intermittent drain passage 85 is not provided. It is only necessary to form an intermittent drain groove 85 having both ends closed on the sliding surface 8 la of the valve plate 81. did Therefore, the intermittent drain passage 85 can be formed easily and inexpensively. Further, since the intermittent drain groove 85 extends in the radial direction of the valve plate 81, it can be easily processed.
  • variable displacement piston pump has been described as an example of the variable displacement piston machine.
  • present invention can be applied to a variable displacement piston motor which is another example of the variable displacement piston machine.
  • the oil guide groove is provided on the sliding surface of the valve plate so as to extend from the suction port toward the top dead center.
  • the intermittent drain passage is provided near the oil guide groove.
  • variable displacement piston machine of the present invention is provided with an oil guide groove extending from the high pressure port toward the dead center on the sliding surface between the low pressure port and the high pressure port of the valve plate.
  • the high-pressure port and the cylinder port communicate with each other through an oil guide groove to gradually change the pressure in the cylinder and the high-pressure port.
  • an intermittent drain passage which is provided so as not to directly communicate with the high pressure port and the oil guide groove. The intermittent drain passage is connected between the high pressure port and the cylinder port.
  • the intermittent drain passage is closed when there is backflow in the oil guide groove, while the intermittent drain passage is closed when there is no backflow in the oil guide groove. Hydraulic oil is discharged from the high-pressure port to the drain through the high-pressure port through the port, reducing pulsation in the high-pressure port, reducing noise and vibration, and improving the operating characteristics of the entire device. be able to. Further, the variable displacement type piston machine of the present invention has a structure in which the intermittent drain passage intermittently communicates with the cylinder port and does not always generate a drain flow. High volumetric efficiency.
  • the intermittent drain passage includes a first intermittent drain passage portion and a second intermittent drain passage portion.
  • the first intermittent drain passage portion includes the cylinder.
  • the second high-pressure port communicates with the high-pressure port via the cylinder port, and the second intermittent drain passage does not communicate with the cylinder port.
  • both the first intermittent drain passage and the second intermittent drain passage communicate with the cylinder port and the high-pressure port via the cylinder port.
  • the second intermittent drain passage communicates with the cylinder port and communicates with the high-pressure port through the cylinder port. Communicated with, the first intermittent drain passage part is adapted to not communicated with the cylinder Bo Bok.
  • the first and second intermittent drain passages control the drain flow in two stages according to the amount of backflow flowing in the oil guide groove, and the sum of the amount of backflow and the flow of drain is almost constant.
  • the pulsation in the high pressure port can be further reduced.
  • the intermittent drain passage is provided on the sliding surface of the valve plate, and is intermittently communicated with the cylinder port intermittently as the cylinder block rotates.
  • the cylinder block slides against the sliding surface of the valve plate, and the valve plate receives small shocks and vibrations from the cylinder block. It can be easily removed even if it is clogged.
  • the first intermittent drain passage and the second intermittent drain passage are respectively provided with a first intermittent drain groove and a second intermittent drain provided on the sliding surface of the valve plate. Since the cylinder block slides against the sliding surface of the valve plate and the valve plate receives small shocks and vibrations from the cylinder block, the first and second intermittent drain grooves have dust and foreign matter. Are hard to clog, and even if clogged, they can be easily removed.
  • the intermittent drain passage communicates with the intermittent drain groove provided on the sliding surface of the valve plate and the intermittent drain groove, and penetrates the valve plate in the axial direction. And a through hole communicating with the drain. Therefore, the cylinder block slides in the intermittent drain groove on the sliding surface with slight vibration, so that dust and the like are hardly clogged, and even if clogged, it can be easily removed. Furthermore, the hydraulic oil is discharged from the intermittent drain groove to the drain through a through hole that penetrates the valve plate in the axial direction, so that the flow direction of the hydraulic oil is changed at the connection point between the intermittent drain groove and the through hole. As a result, energy is consumed, so that noise at the time of discharging hydraulic oil to a drain or the like can be reduced.
  • the intermittent drain passage is provided only on the sliding surface of the valve plate and includes only the intermittent drain groove opened on the peripheral surface of the valve plate, Clogging due to refuse is unlikely to occur, and refuse can be easily removed.
  • variable displacement type piston machine of the embodiment since the intermittent drain passage is formed only of the through hole penetrating the valve plate, the machining of the intermittent drain passage becomes easy.
  • the intermittent drain passage is As the cylinder block rotates, it has a plurality of intermittent drain grooves that communicate with the cylinder port sequentially, so the amount of hydraulic oil discharged to the drain through the intermittent drain passage is determined by the amount of backflow in the oil guide grooves. Can be controlled in multiple stages according to Therefore, pulsation, vibration and noise can be further reduced.
  • variable displacement biston machine of one embodiment since the plurality of intermittent drain grooves are parallel to each other, it is easy to machine the intermittent drain grooves.
  • the intermittent drain passage includes: an intermittent drain through hole that penetrates the valve plate in the axial direction and opens on the sliding surface and the back surface;
  • the intermittent drain through hole and the groove communicating with the drain the amount of intermittent drain can be regulated by the groove on the back surface, and therefore, the diameter of the intermittent drain through hole is increased.
  • the clogging can be prevented.
  • the groove for regulating the amount of intermittent drain is provided on the back surface of the valve plate and not on the sliding surface, the dimensions do not change even if the sliding surface is worn. Therefore, according to this embodiment, the intermittent drain amount is not affected by the wear of the sliding surface of the valve plate.
  • the sliding surface of the valve plate is a part of a spherical surface
  • the back surface of the valve plate is a flat surface
  • the sliding surface of the cylinder plate is the valve plate. Since it is a part of the spherical surface fitted to the sliding surface, it is not necessary to provide a groove for the intermittent drain passage on the sliding surface which is a part of the spherical surface, so that the processing of the intermittent drain passage becomes easy.
  • the intermittent drain passage is provided on the sliding surface of the valve plate and is closed at both ends.
  • the intermittent drain groove is formed on the sliding surface of the cylinder block and is always in communication with the annular groove communicating with the drain. Energy is gradually attenuated while draining through the groove to the drain, thus reducing noise. Since the annular groove of the cylinder block is originally provided to balance the pressure between the cylinder block and the valve plate, the intermittent drain passage is provided at both ends of the sliding surface of the valve plate. It is only necessary to form a closed intermittent drain groove. Therefore, the intermittent drain passage can be formed easily and inexpensively.
  • the intermittent drain groove extends substantially in the radial direction of the valve plate, and the outer end of the intermittent drain groove communicates with the annular groove. Intermittent drain grooves extending in the radial direction can be easily machined.
  • variable displacement piston machine of the present invention is used as a variable displacement piston pump or a variable displacement piston motor in construction machines, machine tools, industrial machines and the like.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)

Abstract

Une machine à piston à déplacement variable sert à limiter le bruit et les vibrations par diminution des pulsations de l'huile d'évacuation au moyen de la réduction de la modification de volume du liquide s'écoulant depuis un orifice à pression élevée vers un orifice à pression basse et un conduit d'évacuation. Un trajet d'évacuation intermittent (5) est constitué dans une surface coulissante (1a) d'une plaque de soupape, de manière à ne pas communiquer directement avec un orifice à pression élevée (3a) et avec une rainure de guidage de l'huile (4). Ce trajet d'évacuation intermittent (5) ne communique pas avec l'orifice à pression élevée (3a) et avec un orifice de cylindre (54a), tandis que s'effectue un écoulement inverse depuis l'orifice à pression élevée (3a) vers l'orifice de cylindre (54a), l'orifice à pression élevée (3a) communiquant avec l'orifice de cylindre (54a) par l'intermédiaire de la rainure de guidage de l'huile (4a). Quand un bloc de cylindre (55) tourne au-delà de cet état, le trajet d'évacuation intermittent (5) communique avec l'orifice à pression élevée (3a) par l'intermédiaire de l'orifice de cylindre (54a).
PCT/JP1996/000238 1995-02-10 1996-02-06 Machine a piston a deplacement variable servant a limiter le bruit et les vibrations par diminution des pulsations du liquide d'evacuation WO1996024765A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
KR1019960705689A KR100253947B1 (ko) 1995-02-10 1996-02-06 토출유체의 맥동을 감소시켜 소음, 진동을 감소시킨 가변용량형 피스톤기계
US08/722,132 US5807080A (en) 1995-02-10 1996-02-06 Variable displacement type piston machine of which noise and vibration are reduced by reducing pulsation of discharge fluid
EP96901543A EP0756084A4 (fr) 1995-02-10 1996-02-06 Machine a piston a deplacement variable servant a limiter le bruit et les vibrations par diminution des pulsations du liquide d'evacuation

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP7/22608 1995-02-10
JP2260895 1995-02-10
JP25745695A JP3362576B2 (ja) 1995-02-10 1995-10-04 可変容量形ピストン機械
JP7/257456 1995-10-04

Publications (1)

Publication Number Publication Date
WO1996024765A1 true WO1996024765A1 (fr) 1996-08-15

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PCT/JP1996/000238 WO1996024765A1 (fr) 1995-02-10 1996-02-06 Machine a piston a deplacement variable servant a limiter le bruit et les vibrations par diminution des pulsations du liquide d'evacuation

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Country Link
WO (1) WO1996024765A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
TWI562911B (en) * 2013-01-29 2016-12-21 Iseki Agricult Mach Work vehicle

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS566080A (en) * 1979-06-25 1981-01-22 Kayaba Ind Co Ltd Axial piston pump
JPS597786A (ja) * 1982-07-07 1984-01-14 Mitsubishi Heavy Ind Ltd ピストン型流体機械
JPH0495671U (fr) * 1991-01-22 1992-08-19

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS566080A (en) * 1979-06-25 1981-01-22 Kayaba Ind Co Ltd Axial piston pump
JPS597786A (ja) * 1982-07-07 1984-01-14 Mitsubishi Heavy Ind Ltd ピストン型流体機械
JPH0495671U (fr) * 1991-01-22 1992-08-19

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP0756084A4 *

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
TWI562911B (en) * 2013-01-29 2016-12-21 Iseki Agricult Mach Work vehicle

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