CN111336080A - Hydraulic pump assembly - Google Patents
Hydraulic pump assembly Download PDFInfo
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- CN111336080A CN111336080A CN201911317494.5A CN201911317494A CN111336080A CN 111336080 A CN111336080 A CN 111336080A CN 201911317494 A CN201911317494 A CN 201911317494A CN 111336080 A CN111336080 A CN 111336080A
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- control
- pressure
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- valve
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- 238000000034 method Methods 0.000 claims abstract description 52
- 239000010720 hydraulic oil Substances 0.000 claims description 17
- 239000003921 oil Substances 0.000 claims description 11
- 230000007257 malfunction Effects 0.000 claims description 5
- 238000006073 displacement reaction Methods 0.000 description 6
- 230000001276 controlling effect Effects 0.000 description 5
- 238000010586 diagram Methods 0.000 description 5
- 239000012530 fluid Substances 0.000 description 4
- 230000013011 mating Effects 0.000 description 4
- 238000010276 construction Methods 0.000 description 3
- 238000012986 modification Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 230000000694 effects Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
Images
Classifications
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- 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
- F04B1/26—Control
- F04B1/28—Control of machines or pumps with stationary cylinders
- F04B1/29—Control of machines or pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
- F04B1/295—Control of machines or pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block by changing the inclination of the swash plate
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- 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
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/14—Control
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- 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
- F04B1/14—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 stationary cylinders
- F04B1/141—Details or component parts
- F04B1/145—Housings
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- 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
- F04B1/2064—Housings
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- 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
- F04B1/26—Control
- F04B1/30—Control of machines or pumps with rotary cylinder blocks
- F04B1/32—Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block
- F04B1/324—Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block by changing the inclination of the swash plate
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- 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
- F04B23/00—Pumping installations or systems
- F04B23/04—Combinations of two or more pumps
- F04B23/06—Combinations of two or more pumps the pumps being all of reciprocating positive-displacement type
-
- G—PHYSICS
- G05—CONTROLLING; REGULATING
- G05D—SYSTEMS FOR CONTROLLING OR REGULATING NON-ELECTRIC VARIABLES
- G05D7/00—Control of flow
- G05D7/06—Control of flow characterised by the use of electric means
- G05D7/0617—Control of flow characterised by the use of electric means specially adapted for fluid materials
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- General Physics & Mathematics (AREA)
- Automation & Control Theory (AREA)
- Reciprocating Pumps (AREA)
- Control Of Positive-Displacement Pumps (AREA)
Abstract
A hydraulic pump assembly of an embodiment of the present invention includes: a common pump housing to which one of different regulators of various control methods is detachably and replaceably coupled, and in which a first flow path capable of transmitting a pressure signal to one or more of the regulator and a small diameter portion of a swash plate drive plunger and a second flow path capable of transmitting another pressure signal to the regulator are formed; and a common valve housing having one area detachably and replaceably coupled to one valve block selected from among different valve blocks for control systems, and the other area coupled to the common pump housing and having a third flow path connecting the valve block and the first flow path and a fourth flow path connecting the valve block and the second flow path formed therein.
Description
Technical Field
The present invention relates to a hydraulic pump assembly, and more particularly, to a hydraulic pump assembly including a variable displacement type hydraulic pump and a regulator.
Background
Generally, a variable displacement hydraulic pump is used in a construction machine, an industrial vehicle, or the like. Such a variable displacement hydraulic pump is driven by an engine, and a discharge flow rate is controlled by a flow rate control device such as a regulator.
For example, when a pair of variable displacement hydraulic pumps are used, regulators are provided for the pair of variable displacement hydraulic pumps, respectively, and the regulators control swash plate angles of the hydraulic pumps in accordance with discharge pressures of the hydraulic pumps on both sides, so as to prevent a sum of horsepower of the hydraulic pumps on both sides from exceeding horsepower of an engine that drives the pair of hydraulic pumps at the same time. In particular, if the input horsepower of the hydraulic pump exceeds the output of the engine, the engine may be stopped by an overload, and it is necessary to appropriately control the discharge flow rate of the hydraulic pump.
Further, recently, regulators using electronically controlled valves are also widely used. Since the discharge flow rate of the hydraulic pump can be controlled by the electronic control valve using the electric signal generated by the control device, flow rate control in various fields can be easily performed, and the discharge flow rate can be accurately controlled. Thus, the efficiency of the hydraulic pump can be improved, and the mechanical structure can be simplified.
On the other hand, as the control method of the hydraulic pump, there are a full horsepower control method, an electronic flow rate control method, an electronic pressure control method, and the like.
The full horsepower control method is a method of automatically reducing the swash plate angle of the hydraulic pump in accordance with the increase in the discharge pressure of the hydraulic pump to control the input torque (torque) to a predetermined value or less. Here, the swash plate angle refers to an angle formed by the swash plate of the hydraulic pump with respect to the drive shaft. The closer the swash plate is erected to the right angle with respect to the drive shaft, the smaller the discharge flow rate of the hydraulic pump, the smaller the intersection angle between the swash plate and the drive shaft, and the larger the discharge flow rate of the hydraulic pump. Further, the horsepower of each of the pair of hydraulic pumps may be controlled by summing up.
In the electronic flow rate control system, a pilot pressure is generated by an electronic control valve using an electric signal generated by a control device, and a swash plate angle of a hydraulic pump is adjusted according to the pilot pressure, thereby adjusting a discharge flow rate of the hydraulic pump.
In the electronic pressure control mode, a regulator supplies pressure to a swash plate drive plunger in accordance with an electric signal. Unlike the electronic flow control approach, the electronic pressure control approach controls without receiving feedback from the swashplate angle.
However, such a control method differs depending on the type of construction machine on which the hydraulic pump is mounted and the selection of the user, and there is a need for a method of easily changing the control method of the hydraulic pump according to the selection of the user, instead of fixing the control method of the single hydraulic pump. However, since the control method of the conventional hydraulic pump is fixed, it has been necessary to replace all the hydraulic pumps when changing the control method.
In addition, since the hydraulic pump is conventionally manufactured in a predetermined state from the beginning in a control method of the hydraulic pump, it is not possible to change the hydraulic pump which has been manufactured once to another method. That is, there is a problem that the more the control method of the hydraulic pump is, the lower the productivity and the manufacturability are.
Disclosure of Invention
Technical subject
Embodiments of the present invention provide a hydraulic pump assembly that is easy to change a regulator to change a control method, and that is manufactured by differentiating a common component from a replaceable component, thereby improving productivity.
Technical scheme
According to an embodiment of the invention, a hydraulic pump assembly comprises: a regulator of a full horsepower control method, a regulator of an electronic pressure control method, a regulator of an electronic flow control method, or a regulator of an electronic flow control method having an emergency drive function; a hydraulic pump having a swash plate; a swash plate driving plunger that moves the swash plate according to control of the regulator; a valve block for a full horsepower control method, a valve block for an electronic pressure control method, a valve block for an electronic flow control method, or a valve block for an electronic flow control method having an emergency drive function; a common pump housing in which one of the full-horsepower control-type regulator, the electronic pressure control-type regulator, the electronic flow rate control-type regulator, and the emergency drive-function regulator is detachably and replaceably coupled, and in which a first passage capable of transmitting a pressure signal to one or more of the regulator and a small-diameter portion of a swash plate drive plunger and a second passage capable of transmitting another pressure signal to the regulator are formed, and the hydraulic pump and the swash plate drive plunger are accommodated; and a common valve casing having an area to which one valve block selected from the full horsepower control type valve block, the electronic pressure control type valve block, the electronic flow rate control type valve block, and the electronic flow rate control type valve block having the emergency drive function is detachably and replaceably coupled, and another area to which the common pump casing is coupled, and having a third flow path connecting the valve block and the first flow path and a fourth flow path connecting the valve block and the second flow path formed therein.
A pair of the hydraulic pumps, a pair of the swash plate drive plungers, and a pair of the regulators may be provided. The pressure of the hydraulic fluid discharged from one of the pair of hydraulic pumps may be referred to as the own pressure, and the pressure of the hydraulic fluid discharged from the other of the pair of hydraulic pumps may be referred to as the opposite pressure. Further, a fifth flow path for transmitting the own pressure to the valve block may be formed in the common pump case, and a sixth flow path and a seventh flow path for transmitting the partner pressure to the regulator may be formed in the common pump case and the common valve case, respectively. The hydraulic pump assembly may further include: and a pilot pump that is provided inside the pump housing and generates a servo pressure.
The full horsepower control style regulator may include: a horsepower control spool that regulates working oil supplied to the large diameter portion of the swash plate drive plunger; a compensator plunger that pressurizes one end of the horsepower control spool; and a horsepower control spring elastically pressurizing the other end portion of the horsepower control valve body.
The valve block for a full horsepower control scheme may include: an electronic control valve that generates a pilot pressure by switching the servo pressure in accordance with an input current; and a shuttle valve that transmits a greater pressure of the servo pressure and the self pressure supplied through the fifth flow path to the third flow path.
Further, the compensator plunger can be supplied with a higher pressure of the servo pressure and the self pressure supplied through the fifth flow path, with the servo pressure and the self pressure supplied through the sixth flow path, with the partner pressure being supplied through the sixth flow path and the seventh flow path, and with the pilot pressure being supplied through the second flow path and the fourth flow path.
The electronic pressure control type regulator may include: a pressure control spool that regulates working oil supplied to the large-diameter portion of the swash plate drive plunger, and one end portion of the pressure control spool is connected to the second flow path; and an electronic control valve that supplies a pilot pressure generated by converting the servo pressure in accordance with an input current to the other end portion of the pressure control spool.
The electronic pressure control type valve block may include: a first block channel connecting the fifth channel and the third channel; a second block channel connecting the fifth channel and the fourth channel; and a check valve provided in the first flow path and controlling the flow of the hydraulic oil only in the direction of the third flow path.
The regulator of the electronic flow control manner may include: an electronic control valve that generates a pilot pressure by switching the servo pressure in accordance with an input current; a flow control spool that regulates working oil supplied to the large diameter portion of the swash plate drive plunger; a pilot plunger that pressurizes one end portion of the flow control spool in accordance with the pilot pressure; and a pilot control spring elastically pressurizing the other end portion of the flow rate control spool.
The valve block for an electronic flow control system may include: a block channel connecting the fifth channel and the third channel; and a check valve provided in the block flow path and controlling the flow of the hydraulic oil only in the direction of the third flow path.
The electronic flow control type regulator with the emergency driving function may include: an electronic control valve that generates a pilot pressure by switching the servo pressure in accordance with an input current; a main control line for communicating the servo pressure to the electronically controlled valve; a flow control spool and a horsepower control spool that regulate working oil supplied to a large diameter portion of the swash plate drive plunger; a pilot plunger that pressurizes one end portion of the flow control spool in accordance with the pilot pressure; a pilot control spring elastically pressurizing the other end portion of the flow rate control spool; a compensator plunger that moves the horsepower control valve spool by pressurizing one end portion of the horsepower control valve spool when the servo pressure is introduced through the second flow passage; and a horsepower control spring elastically pressurizing the other end portion of the horsepower control valve body.
The electronic flow control valve block having the emergency driving function may include: a block channel connecting the fifth channel and the third channel; a check valve provided in the block flow path and controlling the flow of the hydraulic oil only in the third flow path direction; and an emergency control line connected to the fourth flow path.
In addition, the hydraulic pump assembly may further include: a servo pressure supply line selectively separably connectable with one of the main control line and the emergency control line to supply the servo pressure.
The servo pressure supply line may be connected to the main control line when the electronic control valve is normally operated; the servo pressure supply line may be connected to the emergency control line by a user's selection when the electronic control valve malfunctions or is unable to do so.
ADVANTAGEOUS EFFECTS OF INVENTION
According to the embodiment of the present invention, the hydraulic pump assembly can be manufactured by dividing the parts which can be commonly used and the replaceable parts, thereby improving productivity, while facilitating the replacement of the regulator to change the control method.
Drawings
FIG. 1 is a perspective view of a hydraulic pump assembly according to an embodiment of the present invention.
Fig. 2 is a hydraulic circuit diagram illustrating a state in which a regulator of the full horsepower control method and a valve block for the full horsepower control method are applied to the hydraulic pump assembly of fig. 1.
Fig. 3 is a hydraulic circuit diagram illustrating states of a regulator to which an electronic pressure control method is applied and a valve block for the electronic pressure control method in the hydraulic pump assembly of fig. 1.
Fig. 4 is a hydraulic circuit diagram illustrating a state in which the regulator of the electronic flow control system and the valve block for the electronic flow control system are applied to the hydraulic pump assembly of fig. 1.
Fig. 5 is a hydraulic circuit diagram illustrating a state in which a regulator of an electronic flow rate control system having an emergency drive function and a valve block for an electronic flow rate control system having an emergency drive function are applied to the hydraulic pump assembly of fig. 1.
Fig. 6 is a hydraulic circuit diagram illustrating a state in which the hydraulic pump assembly of fig. 1 is driven in an emergency.
Description of the symbols
100: hydraulic pump, 130: pilot pump, 150: a swash plate, 170: swash plate drive plunger, 180: feedback lever, 200: regulator, 201: full horsepower control type regulator, 202: electronic pressure control type regulator, 203: electronic flow control type regulator, 204: electronic flow control type regulator with emergency drive function, 250: valve block, 251: valve block for full horsepower control, 252: valve block for electronic pressure control mode, 253: valve block for electronic flow control system, 254: electronic flow control system valve block having emergency drive function, 311: flow control spool, 312: horsepower control spool, 321: flow control sleeve, 322: horsepower control sleeve, 330: pilot control spring, 340: horsepower control spring, 350: pilot plunger, 370: compensator plunger, 500: electronic control valve, 610: main control line, 620: emergency control line, 630: servo pressure supply line, 651: first flow path, 652: second flow path, 653: third flow path, 654: fourth flow path, 655: fifth flow path, 656: sixth flow path, 657: seventh flow path, 671: first block flow path, 672: second block flow path, 680, 690: block flow path, 760: shuttle valve, 770, 780, 790: a check valve.
Detailed Description
Embodiments of the present invention will be described in detail below with reference to the accompanying drawings so that those skilled in the art can easily practice the invention. The invention may be embodied in many different forms and is not limited to the embodiments described herein.
It is noted that the drawings are diagrammatic and not to scale. Relative dimensions and proportions of parts shown in the figures have been shown exaggerated or reduced in size for the sake of clarity and convenience in the drawings, and any dimensions are exemplary only and not limiting. In addition, the same reference numerals are used for the same structures, elements or components appearing in two or more drawings to represent similar features.
The embodiments of the present invention specifically show desirable embodiments of the present invention. As a result, various modifications of the illustration are expected. Thus, embodiments are not limited to the particular manner of area illustrated, but, for example, also include variations of the manner in which the manufacture is effected.
A hydraulic pump assembly 101 according to an embodiment of the present invention will be described with reference to fig. 1 to 6.
As illustrated in fig. 1 to 6, a hydraulic pump assembly 101 according to an embodiment of the present invention includes one regulator 200 selected from among a plurality of regulators 200 having different control methods from each other, one valve block 250 selected from among a plurality of valve blocks 250 having different structures from each other, a common pump housing 810, a hydraulic pump 100, a swash plate driving plunger 170, and a common valve housing 850.
The hydraulic pump 100 is provided inside a common pump case 810 to be described later, and has a swash plate 150 for variable displacement-varying a discharge displacement. Further, in an embodiment of the present invention, a pair of hydraulic pumps 100 may be used, and the pair of hydraulic pumps 100 may be respectively controlled by a pair of regulators 200 having the same control manner. In fig. 2 to 6, only 1 hydraulic pump 100 out of the pair of hydraulic pumps 100 is shown, and the discharge pressure of the hydraulic pump 100 is referred to as "self pressure Pd" and the discharge pressure of the other hydraulic pump is referred to as "counter pressure P2". That is, the pressure of the hydraulic fluid discharged from one of the hydraulic pumps 100 in the pair of hydraulic pumps 100 is referred to as the own pressure Pd, and the pressure of the hydraulic fluid discharged from the other hydraulic pump 100 in the pair of hydraulic pumps 100 is referred to as the counterpressure P2.
Similarly, a pair of swash plate driving plungers 170 are provided inside a common pump housing 810 to be described later, and the swash plate driving plungers 170 move the swash plate of the hydraulic pump 100 in accordance with control of the regulator 200 to be described later.
The pilot pump 130 generates the servo pressure Psv. Similarly, the pilot pump 130 may be provided inside a common pump case 810 to be described later, and may be connected to and driven by an engine (not shown) together with the pair of hydraulic pumps 100. For example, the pilot pump 130 may be connected in series with the pair of hydraulic pumps 100. That is, when the pair of hydraulic pumps 100 are driven by the engine, the pilot pumps 130 may be driven simultaneously. As the pilot pump 130, a gear pump may be mainly used. However, an embodiment of the present invention is not limited thereto.
The common pump case 810 accommodates the pair of hydraulic pumps 100, the pair of swash plate driving plungers 170, and the pilot pump 130. Further, flow paths 651, 652, 655, and 656 for transmitting various pressure signals are formed inside the common pump case 810.
Specifically, the common pump case 810 may be provided with a first flow path 651 that can transmit a pressure signal to one or more of the regulator 200 and the small diameter portion of the swash plate drive plunger 170, which will be described later, a second flow path 652 that can transmit another pressure signal to the regulator 200, a fifth flow path 655 that transmits the own pressure Pd to the valve block 250, which will be described later, and a sixth flow path 656 that transmits the partner pressure P2 to the regulator 200.
One area of the common valve housing 850 is detachably and replaceably combined with the valve block 250 to be described later, and another area of the common valve housing 850 is combined with the common pump housing 810. In addition, flow paths 653, 654, and 657 for transmitting various pressure signals are formed inside the common valve housing 850.
Specifically, a third flow path 653 that connects the valve block 250 and the first flow path 651 of the common pump case 810, which will be described later, a fourth flow path 654 that connects the valve block 250 and the second flow path 652 of the common pump case 810, and a seventh flow path 657 that connects the sixth flow path 656 of the common pump case 810 to transmit the partner pressure P2 to the regulator 200 may be formed in the common valve housing 850.
The plurality of regulators 200 having different control modes from each other may be selected from a regulator 201 of a full horsepower control mode, a regulator 202 of an electronic pressure control mode, a regulator 203 of an electronic flow control mode, and a regulator 204 of an electronic flow control mode having an emergency drive function. That is, any one of the regulators 200 selected from the group consisting of the regulator 201 of the full horsepower control method, the regulator 202 of the electronic pressure control method, the regulator 203 of the electronic flow rate control method, and the regulator 204 of the electronic flow rate control method having the emergency drive function may be detachably and replaceably coupled to the common pump case 810.
The plurality of valve blocks 250 having different structures may be selected from a valve block 251 for a full horsepower control system, a valve block 252 for an electronic pressure control system, a valve block 253 for an electronic flow control system, or a valve block 254 for an electronic flow control system having an emergency driving function. That is, any one of the valve blocks 250 selected from the valve block 251 for the full horsepower control method, the valve block 252 for the electronic pressure control method, the valve block 253 for the electronic flow control method, and the valve block 254 for the electronic flow control method having the emergency drive function may be detachably and replaceably coupled to the common valve casing 850.
As illustrated in fig. 2, in the aforementioned plurality of regulators 200, the regulator 201 of the full horsepower control scheme may include a horsepower control spool 312, a compensator (compensator) plunger 370, a horsepower control spring 340, a horsepower control sleeve 322, and a feedback lever 9180.
Further, among the aforementioned plurality of valve blocks, the valve block 251 for the full horsepower control method includes the electronic control valve 500 and the shuttle valve (760).
The horsepower control spool 312 controls the action of the swash plate drive plunger 170 by regulating the working oil supplied to the large diameter portion of the swash plate drive plunger 170. Here, controlling the action of the swash plate driving plunger 170 means adjusting the angle of the swash plate 150 to adjust the discharge flow rate of the hydraulic pump 100.
The electronic control valve 500 generates the pilot pressure Pi by switching the servo pressure Psv in accordance with the input current.
The shuttle valve 760 transmits the greater pressure of the servo pressure Psv and the self pressure Pd supplied through the fifth flow path 655 to the third flow path 653. Then, the pressure is directed toward the horsepower control valve element 312 and the small diameter portion of the swash plate drive plunger 170 via the first flow path 651.
The compensator plunger 370 pressurizes one end of the horsepower control spool 312 according to the pilot pressure Pi to move the horsepower control spool 312. Specifically, the larger of the servo pressure Psv and the self pressure Pd supplied through the fifth flow path 655 is introduced into the compensator plunger 370 through the first flow path 651, the counter pressure P2 is introduced through the sixth flow path 656 and the seventh flow path 657, and the pilot pressure Pi is introduced through the second flow path 652 and the fourth flow path 654.
The horsepower control spring 340 elastically pressurizes the other end portion of the horsepower control valve spool 312. In this case, the horsepower control spring 340 may be configured as 2 springs, and the horsepower control line that changes in the middle of the change gradient according to the flow rate may be approximated to the horsepower line.
As such, the position of the horsepower control valve spool 312 is determined by various pressures including the pilot pressure Pi introduced to the compensator plunger 370 and the elastic force of the horsepower control spring 340. That is, since the pressure introduced to the compensator plunger 370 can be set by the electronic control valve 500, the horsepower of the hydraulic pump 100 can be controlled by an electric signal.
The horsepower control sleeve 322 may wrap around the horsepower control spool 312 to form a variable orifice in a position opposite the horsepower control spool 312.
The feedback lever 200 may mechanically connect the horsepower control sleeve 322 with the swash plate drive plunger 170 and feed back the angle of the swash plate 150. That is, when the swash plate drive plunger 170 moves, the feedback lever 180 moves, and accordingly, the horsepower control sleeve 322 moves in the axial direction. Thus, the position of the horsepower control sleeve 322 is determined according to the angle of the swash plate 150.
As illustrated in fig. 3, in the plurality of regulators 200, the electronic pressure control type regulator 202 includes the pressure control spool 380 and the electronic control valve 500.
In the plurality of valve blocks 250, the electronic pressure control valve block 252 includes a first block flow path 671, a second block flow path 672, and a check valve 770.
The pressure control spool 380 regulates the hydraulic oil supplied to the large diameter portion of the swash plate drive plunger 170, and has one end connected to the second flow passage 652.
The electronic control valve 500 supplies a pilot pressure Pi, which is generated by converting the servo pressure Psv in accordance with an input current, to the other end portion of the pressure control spool 380.
The first block flow path 671 connects the fifth flow path 655 with the third flow path 653. The third flow path 653 is connected to the first flow path 651, and moves the servo pressure Psv passing through the first block flow path 671 along the first flow path 651 toward the pressure control spool 380 and the small diameter portion of the swash plate driving plunger 170. The check valve 770 is provided in the first block flow path 671 and controls the flow of the hydraulic oil only in the direction of the third flow path 653.
The second block flow path 672 connects the fifth flow path 655 and the fourth flow path 654. The fourth flow path 654 and the second flow path 652 move the servo pressure Psv that has passed through the second block flow path 672 along the second flow path 652 toward the one end portion of the pressure control spool 380.
Accordingly, when the input current to the electronic control valve 500 increases and the pilot pressure Pi generated by the electronic control valve 500 increases, the hydraulic oil flowing into the large-diameter portion of the swash plate driving plunger 170 increases, and the discharge flow rate of the hydraulic pump increases accordingly.
On the other hand, in the electronic pressure control method, the feedback lever 180 may be omitted. In the electronic pressure control system, the mating pressure P2 is not used, and therefore the sixth flow passage 656 and the seventh flow passage 657 are not used.
As illustrated in fig. 4, in the plurality of regulators 200, the electronic flow control type regulator 203 includes an electronic control valve 500, a flow control spool 311, a pilot plunger 350, a pilot control spring 330, a flow control sleeve 321, and a feedback lever 180.
In the plurality of valve blocks 250, the valve block 253 for an electronic flow control system includes a block flow path 680 and a check valve 780.
The block channel 680 connects the fifth channel 655 and the third channel 653. The third flow path 653 is connected to the first flow path 651, and the servo pressure Psv passing through the block flow path 680 moves along the first flow path 651 toward the pressure control spool 380 and the small diameter portion of the swash plate driving plunger 170. The check valve 780 is provided in the block flow path 680 to control the flow of the hydraulic oil only in the direction of the third flow path 653.
The electronic control valve 500 generates the pilot pressure Pi by switching the servo pressure Psv in accordance with the input current. Flow control spool 311 regulates the working oil supplied to the large diameter portion of swash plate drive plunger 170. The pilot plunger 350 pressurizes one end of the flow control spool according to the pilot pressure Pi. In addition, the pilot control spring 330 elastically pressurizes the other end portion of the flow control spool 311.
Accordingly, when the input current to the electronic control valve 500 increases, the pilot pressure Pi introduced into the pilot plunger 350 increases, and when the flow rate control spool 311 is moved by the pilot plunger 350 in accordance with the pilot pressure Pi, the hydraulic oil supplied to the large diameter portion of the swash plate drive plunger 170 increases, and accordingly, the discharge flow rate of the hydraulic pump 100 increases.
The flow control sleeve 321 may wrap around the flow control spool 311 to form a variable orifice at a position opposite the flow control spool 311.
On the other hand, in the electronic flow rate control system, the mating pressure P2 is not used, and therefore the sixth flow path 656 and the seventh flow path 657 are not used.
As illustrated in fig. 5, among the plurality of regulators 200, the electronic flow control type regulator 204 having the emergency driving function includes an electronic control valve 500, a flow control spool 311, a pilot plunger 350, a pilot control spring 330, a flow control sleeve 321, a horsepower control spool 312, a compensator plunger 370, a horsepower control spring 340, a horsepower control sleeve 322, a main control line 610, and a feedback lever 180.
In addition, in the plurality of valve blocks 250, the electronic flow control type valve block 253 includes a block flow passage 690, a check valve 790, and an emergency control line 620.
In addition, the hydraulic pump assembly 101 may also include a servo pressure supply line 630.
The flow control spool 311 moves according to the pilot pressure Pi to control the hydraulic oil supplied to the swash plate driving plunger 170. Specifically, in the electronic flow control system, the flow control spool 311 is controlled by the pilot pressure Pi generated by switching the servo pressure Psv by the electronic control valve 500. Here, the servo pressure Psv is also referred to as a 1-time pressure, and the pilot pressure Pi is also referred to as a 2-time pressure. For example, when the input current becomes large, the electronic control valve 500 converts the servo pressure Psv into the pilot pressure Pi of a relatively high pressure; when the input current is small, the electronic control valve 500 converts the servo pressure Psv into the pilot pressure Pi of a relatively low pressure. That is, when the input current of the electronic control valve 500 changes, the pilot pressure Pi changes accordingly, and the discharge flow rate of the hydraulic pump 100 can be controlled.
The horsepower control valve spool 312 moves according to the servo pressure Psv and the mating pressure P2 of the hydraulic pump 100 to control the hydraulic oil supplied to the swash plate driving plunger 170. When the discharge pressure of the hydraulic pump 100, i.e., the mating pressure P2, increases, the horsepower control valve body 312 moves to adjust the hydraulic oil supplied to the swash plate drive plunger 170, thereby reducing the tilt angle of the swash plate 150 of the hydraulic pump 100 and controlling the input torque (torque) of the hydraulic pump 150 to a predetermined value or less.
When the pilot pressure Pi generated by the electronic control valve 500 is introduced into the pilot plunger 350, the pilot plunger 350 pressurizes one end portion of the flow rate control spool 311 to move the flow rate control spool 311. Specifically, the pilot plunger 350 pressurizes one end portion of the flow control spool 311 in accordance with the pilot pressure Pi to move the flow control spool 311. In addition, the pilot control spring 330 elastically pressurizes the other end portion of the flow control spool 311. Accordingly, when the pilot pressure Pi becomes larger than the elastic force of the pilot control spring 330, the pilot plunger 350 moves the flow rate control spool 311 in the other end portion direction; when the pilot pressure Pi becomes smaller than the elastic force of the pilot control spring 330, the flow rate control spool 311 moves in the one end direction.
That is, when the electronic control valve 500 raises the pilot pressure Pi introduced into the pilot plunger 350, the flow rate control spool 311 increases the hydraulic oil supplied to the large-diameter portion of the swash plate drive plunger 170, and eventually, the discharge flow rate of the hydraulic pump 100 increases.
When the servo pressure Psv generated by the pilot pump 130 is introduced into the compensator plunger 370, one end of the horsepower control spool 312 is pressurized to move the horsepower control spool 312. Specifically, the servo pressure Psv of the pilot pump 130 and the counter pressure P2 of the hydraulic pump 100 are introduced into the compensator plunger 370, and one end portion of the horsepower control spool 312 is pressurized by this force. In addition, the horsepower control spring 340 elastically pressurizes the other end portion of the horsepower control valve spool 312. In this way, the position of the horsepower control valve body 312 is determined by the servo pressure Psv of the pilot pump 130 introduced into the compensator plunger 370, the opposing pressure P2 of the hydraulic pump 100, and the elastic force of the horsepower control spring 340.
A main control line 610 is provided to transmit the servo pressure Psv generated by the pilot pump 130 to the electronic control valve 500. In addition, an emergency control line 620 is provided to transmit the servo pressure Psv generated by the pilot pump 130 to the compensator plunger 370.
In addition, in an embodiment of the present invention, the servo pressure supply line 630 is selectively separably connected to one of the main control line 610 and the emergency control line 620 to supply the servo pressure Psv generated by the pilot pump 130.
For example, connection ports may be provided at ends of the main control line 610 and the emergency control line 620, and an end of the servo pressure supply line 630 may be provided in the form of a hose, for example. Thus, an end of the servo pressure supply line 630 may be connected to a connection port provided at one end of the main control line 610 and the emergency control line 620, and a connection port provided at the other end may be sealed with a cover. In addition, the user can selectively exchange the end of the servo pressure supply line 630 for another connection port for connection as needed.
Specifically, as illustrated in fig. 5, when the electronic control valve 500 normally operates, the servo pressure supply line 630 is connected to the main control line 610. Thus, the servo pressure Psv is supplied to the electronic control valve 500, so that the electronic control valve 500 can supply the pilot pressure Pi to the pilot spool 350.
Thus, the hydraulic pump 100 can be controlled in an electronic flow control manner. That is, as the current input to the electronic control valve 500 increases, the swash plate angle increases, and the discharge flow rate of the hydraulic pump 100 increases accordingly. Here, the swash plate angle refers to an angle formed by the swash plate 150 of the hydraulic pump 100 with respect to the drive shaft. The closer to a right angle the swash plate 150 stands with respect to the drive shaft, the smaller the discharge flow rate of the hydraulic pump 100, and the smaller the intersection angle between the swash plate 150 and the drive shaft, the more the discharge flow rate of the hydraulic pump 100.
In contrast, as illustrated in fig. 6, when the electronic control valve 500 malfunctions or is unable to do so, the servo pressure supply line 630 may be connected to the control line 620 by a user's selection. That is, when the hydraulic pump 100 fails to operate due to a malfunction of the electronic control valve 500 or an emergency of an electric and electronic system, a user may disconnect the servo pressure supply line 630 from the main control line 610 and then connect it to the emergency control line 620 instead. Then, the compensator plunger 370 moves the horsepower control spool 312 by supplying the servo pressure Psv to the compensator plunger 370 through the emergency control line 620, and accordingly, the horsepower control of the hydraulic pump 100 is enabled. That is, the swash plate angle of the hydraulic pump 100 can be automatically reduced to control the input torque (torque) to a predetermined value or less as the discharge pressure of the hydraulic pump 100 increases. Accordingly, the hydraulic pump 100 can be operated without the engine being turned off. Accordingly, the construction machine to which the hydraulic pump 100 is mounted can be moved to a serviceable area or emergency work can be continuously performed.
Further, as described above, when the servo pressure Psv is introduced into the compensator plunger 370, the servo pressure Psv is also introduced into the pilot plunger 350, and the pilot plunger 350 can move the flow rate control spool 311 to a position that does not affect the control of the swash plate drive plunger 170.
For example, since the servo pressure Psv as the 1 st pressure will have a pressure greater than the pilot pressure Pi as the 2 nd pressure, when the servo pressure Psv directly acts on the pilot plunger 350, the pilot plunger 350 can strongly push the flow rate control spool 311 to move to the end.
The flow control sleeve 321 may wrap around the flow control spool 311 to form a variable orifice at a position opposite the flow control spool 311.
The horsepower control sleeve 322 may wrap around the horsepower control spool 312 to form a variable orifice in a position opposite the horsepower control spool 312.
The feedback lever 200 may mechanically connect the flow control sleeve 321 and the horsepower control sleeve 322 with the swash plate drive plunger 170 and feed back the angle of the swash plate 150. That is, when the swash plate drive plunger 170 moves, the feedback lever 180 moves, and accordingly, the flow control sleeve 321 and the horsepower control sleeve 322 move in the axial direction. Accordingly, the positions of the flow control sleeve 321 and the horsepower control sleeve 322 are determined according to the angle of the swash plate 150.
With such a configuration, the hydraulic pump assembly 101 according to the embodiment of the present invention can be manufactured by easily changing the regulator 200 to change the control method and by dividing the parts that can be commonly used and the parts that can be changed, thereby improving productivity.
Specifically, the control method of the hydraulic pump assembly 101 can be changed by merely replacing the regulator 200 and the valve block 250, and the structures provided in the common pump housing 810, the common valve housing 850, and the common pump housing 810 and the common valve housing 820 can be used accordingly.
Although the embodiments of the present invention have been described above with reference to the drawings, it will be understood by those skilled in the art to which the present invention pertains that the present invention may be embodied in other specific forms without changing the technical idea or essential features of the present invention.
Therefore, the above-described embodiments should be construed as illustrative in all aspects and not restrictive, the scope of the present invention being indicated by the appended claims, and all changes or modifications derived from the meaning and scope of the claims and their equivalents should be construed as falling within the scope of the present invention.
Claims (7)
1. A hydraulic pump assembly, comprising:
a regulator of a full horsepower control method, a regulator of an electronic pressure control method, a regulator of an electronic flow control method, or a regulator of an electronic flow control method having an emergency drive function;
a hydraulic pump having a swash plate;
a swash plate driving plunger that moves the swash plate according to control of the regulator;
a valve block for a full horsepower control method, a valve block for an electronic pressure control method, a valve block for an electronic flow control method, or a valve block for an electronic flow control method having an emergency drive function;
a common pump housing in which one of the full-horsepower control-type regulator, the electronic pressure control-type regulator, the electronic flow rate control-type regulator, and the emergency drive-function regulator is detachably and replaceably coupled, and in which a first passage capable of transmitting a pressure signal to one or more of the regulator and a small-diameter portion of a swash plate drive plunger and a second passage capable of transmitting another pressure signal to the regulator are formed, and the hydraulic pump and the swash plate drive plunger are accommodated; and
and a common valve casing having an area which is detachably and replaceably coupled to one valve block selected from the group consisting of the full-horsepower control valve block, the electronic pressure control valve block, the electronic flow rate control valve block, and the emergency drive function valve block, and another area which is coupled to the common pump casing and in which a third flow path connecting the valve block and the first flow path and a fourth flow path connecting the valve block and the second flow path are formed.
2. The hydraulic pump assembly as recited in claim 1,
a pair of said hydraulic pumps, a pair of said swash plate drive plungers, and a pair of said regulators are provided,
the pressure of the hydraulic oil discharged from one of the pair of hydraulic pumps is called the own pressure, the pressure of the hydraulic oil discharged from the other of the pair of hydraulic pumps is called the opposite pressure,
a fifth flow path for transmitting the own pressure to the valve block is formed in the common pump case,
a sixth flow path and a seventh flow path for transmitting the counterpressure to the regulator are formed in the common pump housing and the common valve housing, respectively,
the hydraulic pump assembly further includes:
and a pilot pump that is provided inside the pump housing and generates a servo pressure.
3. The hydraulic pump assembly of claim 2,
the full horsepower control style regulator includes:
a horsepower control spool that regulates working oil supplied to the large diameter portion of the swash plate drive plunger;
a compensator plunger that pressurizes one end of the horsepower control spool; and
a horsepower control spring elastically pressurizing the other end portion of the horsepower control valve body,
the valve block for a full horsepower control method includes:
an electronic control valve that generates a pilot pressure by switching the servo pressure in accordance with an input current; and
a shuttle valve that transmits a greater pressure of the servo pressure and the self pressure supplied through the fifth flow path to the third flow path,
the compensator plunger is configured to introduce a larger pressure of the servo pressure and the self pressure supplied through the fifth flow path through the first flow path, introduce a counter pressure through the sixth flow path and the seventh flow path, and introduce the pilot pressure through the second flow path and the fourth flow path.
4. The hydraulic pump assembly of claim 2,
the electronic pressure control type regulator includes:
a pressure control spool that regulates working oil supplied to the large-diameter portion of the swash plate drive plunger, and one end portion of the pressure control spool is connected to the second flow path; and
an electronic control valve that supplies a pilot pressure generated by converting the servo pressure in accordance with an input current to the other end portion of the pressure control spool,
the electronic pressure control mode valve block includes:
a first block channel connecting the fifth channel and the third channel;
a second block channel connecting the fifth channel and the fourth channel; and
and a check valve provided in the first flow path and controlling the flow of the hydraulic oil only in the direction of the third flow path.
5. The hydraulic pump assembly of claim 2,
the regulator of the electronic flow control mode comprises:
an electronic control valve that generates a pilot pressure by switching the servo pressure in accordance with an input current;
a flow control spool that regulates working oil supplied to the large diameter portion of the swash plate drive plunger;
a pilot plunger that pressurizes one end portion of the flow control spool in accordance with the pilot pressure; and
a pilot control spring elastically pressurizing the other end portion of the flow rate control spool,
the valve block for an electronic flow control system includes:
a block channel connecting the fifth channel and the third channel; and
and a check valve provided in the block flow path and controlling the flow of the hydraulic oil only in the third flow path direction.
6. The hydraulic pump assembly of claim 2,
the electronic flow control type regulator with the emergency driving function comprises:
an electronic control valve that generates a pilot pressure by switching the servo pressure in accordance with an input current;
a main control line for communicating the servo pressure to the electronically controlled valve;
a flow control spool and a horsepower control spool that regulate working oil supplied to a large diameter portion of the swash plate drive plunger;
a pilot plunger that pressurizes one end portion of the flow control spool in accordance with the pilot pressure;
a pilot control spring elastically pressurizing the other end portion of the flow rate control spool;
a compensator plunger that moves the horsepower control valve spool by pressurizing one end portion of the horsepower control valve spool when the servo pressure is introduced through the second flow passage; and
a horsepower control spring elastically pressurizing the other end portion of the horsepower control valve body,
the valve block for electronic flow control with emergency driving function comprises,
a block channel connecting the fifth channel and the third channel;
a check valve provided in the block flow path and controlling the flow of the hydraulic oil only in the third flow path direction; and
an emergency control line connected to the fourth flow path,
the hydraulic pump assembly further includes:
a servo pressure supply line selectively separably connectable with one of the main control line and the emergency control line to supply the servo pressure.
7. The hydraulic pump assembly as in claim 6,
when the electronic control valve works normally, the servo pressure supply pipeline is connected with the main control pipeline;
when the electronic control valve malfunctions or is unable to do so, the servo pressure supply line is connected to the emergency control line by a user's selection.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| KR1020180165504A KR102172626B1 (en) | 2018-12-19 | 2018-12-19 | Hydraulic pump assembly |
| KR10-2018-0165504 | 2018-12-19 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN111336080A true CN111336080A (en) | 2020-06-26 |
| CN111336080B CN111336080B (en) | 2022-03-01 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201911317494.5A Active CN111336080B (en) | 2018-12-19 | 2019-12-19 | Hydraulic pump assembly |
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| Country | Link |
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| KR (1) | KR102172626B1 (en) |
| CN (1) | CN111336080B (en) |
Families Citing this family (1)
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| KR20220078335A (en) * | 2020-12-03 | 2022-06-10 | 현대두산인프라코어(주) | Hydraulic system |
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| JP6550297B2 (en) * | 2015-08-07 | 2019-07-24 | 川崎重工業株式会社 | Hydraulic drive system |
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- 2018-12-19 KR KR1020180165504A patent/KR102172626B1/en active IP Right Grant
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| US3625240A (en) * | 1969-05-16 | 1971-12-07 | Bendix Corp | Hydraulic booster system |
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Also Published As
| Publication number | Publication date |
|---|---|
| KR20200076417A (en) | 2020-06-29 |
| KR102172626B1 (en) | 2020-11-02 |
| CN111336080B (en) | 2022-03-01 |
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